Vehicle air conditioner control method, electronic equipment and storage medium

Abstract

The invention discloses a vehicle air conditioner control method, electronic equipment and a storage medium, and relates to the technical field of vehicles. The method comprises the steps that in response to an air conditioner starting instruction, the vehicle exterior environment temperature is collected, and whether the vehicle exterior environment temperature is within a preset working condition temperature interval or not is determined; if yes, a compressor is started, and the target air outlet temperature of the indoor heat exchanger is determined according to temperature control information contained in the air conditioner starting instruction; and the opening degree of the second expansion valve is determined according to the actual air outlet temperature and the target air outlet temperature, so that control over the air outlet temperature is achieved. Dynamic distribution of refrigerant circulation is achieved through a multi-heat-exchanger collaborative architecture and an intelligent algorithm, and on the premise that PTC intervention is not needed, evaporation temperature stability and outlet air temperature accurate control are synchronously optimized.

Description

Technical Field

[0001] This application relates to the technical field of vehicles, and in particular, to a vehicle air-conditioning control method, an electronic device, and a storage medium. Background Art

[0002] With the rapid development of new energy vehicles, the energy efficiency and comfort requirements of vehicle air-conditioning systems are increasing day by day. Traditional single-cooling air-conditioning systems rely on electric auxiliary heating devices (PTC, Positive Temperature Coefficient) for temperature adjustment, and there are problems such as excessive energy consumption in low-temperature environments; although heat pump systems can improve heating efficiency, they still require PTC auxiliary heating during high-temperature dehumidification, and there are inherent contradictions in the frequent switching between the refrigeration mode and the heat pump mode and the difficulty in coordinating the outlet air temperature and the dehumidification efficiency under low-temperature dehumidification conditions.

[0003] Existing technologies generally adopt a fixed evaporation temperature threshold and a single expansion valve control strategy, which cannot dynamically balance the low-temperature evaporator operation required for dehumidification and the high outlet air temperature required for comfort, resulting in poor system stability and low energy efficiency. To address the above problems, a new control method is urgently needed to realize the dynamic distribution of the refrigerant cycle through a multi-heat exchanger collaborative architecture and an intelligent algorithm, and synchronously optimize the evaporation temperature stability and the accurate control of the outlet air temperature without the intervention of PTC, so as to fundamentally solve the technical bottleneck that it is difficult to balance energy efficiency and comfort. Summary of the Invention

[0004] In view of the above problems, the present disclosure provides a vehicle air-conditioning control method, an electronic device, and a storage medium that overcome the above problems or at least partially solve the above problems. The technical solutions are as follows:

[0005] A vehicle air-conditioning control method is applied to a vehicle air-conditioning control system. The system includes: 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. 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 pipeline connecting the intermediate heat exchange device 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 arranged between the intermediate heat exchange device and the indoor heat exchanger. The method includes:

[0006] In response to an air-conditioning start command, collect the outside ambient temperature of the vehicle, and determine whether the outside ambient temperature is within a preset operating condition temperature range;

[0007] If so, start the compressor, and determine the target outlet air temperature of the indoor heat exchanger according to the temperature control information included in the air-conditioning start command;

[0008] Determine the opening degree of the second expansion valve according to the actual outlet air temperature and the target outlet air temperature, so as to control the outlet air temperature.

[0009] A vehicle air conditioner control method provided by the present disclosure, by setting a cooperative architecture of a dual expansion valve and three heat exchangers, dynamically determines whether to enter a preset working condition temperature range based on the outside vehicle environment temperature, and combines the target outlet air temperature to adjust the opening degree of the second expansion valve, realizing fine allocation of the refrigerant cycle. This solution directly controls the outlet air temperature of the indoor heat exchanger through the second expansion valve, avoiding the energy consumption waste caused by relying on PTC heating in the traditional system. At the same time, by using the linkage adjustment of the compressor and the dual valves, the stability of the outlet air temperature is significantly improved on the premise of ensuring the dehumidification efficiency, solving the core contradiction that it is difficult to balance the dehumidification demand and comfort in the prior art.

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

[0011] Calculate the target temperature difference of the outlet air according to the actual outlet air temperature and the target outlet air temperature, and determine whether the target temperature difference of the outlet air is within a preset stable range of the outlet air temperature;

[0012] If not, determine the opening degree adjustment step of the second expansion valve according to the corresponding relationship between the target temperature difference of the outlet air 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;

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

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

[0015] In this embodiment, through the corresponding relationship between the target temperature difference of the outlet air and the opening degree adjustment step of the second expansion valve and the phased maintenance control strategy, when the target temperature difference of the outlet air exceeds the stable range, a differential step adjustment and time holding mechanism are adopted, which can not only quickly converge to the target temperature when the temperature difference is large, but also avoid overshoot oscillation when approaching the stable range. This control logic effectively improves the response speed and steady-state accuracy of the outlet air temperature control by combining dynamic step adjustment and forced holding time, and at the same time reduces the risk of system fluctuations caused by frequent adjustment.

[0016] Optionally, the method further includes:

[0017] Obtain the target evaporation temperature of the evaporator according to the dehumidification information included in the air conditioner start instruction;

[0018] Control the opening degree of the first expansion valve according to the target evaporation temperature and the opening degree of the second expansion valve, and obtain the actual evaporator temperature, so as to determine the rotational speed of the compressor according to the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature.

[0019] In this embodiment, through the introduction of the linkage control of the target evaporation temperature of the evaporator and the opening degree of the second expansion valve, combined with the dynamic adjustment of the rotational speed of the compressor, a three-dimensional collaborative control system of evaporation temperature - outlet air temperature - compressor rotational speed is constructed. This design enables the opening degree adjustment of the first expansion valve to synchronously respond to the dehumidification demand and the change of the outlet air temperature. While ensuring the low-temperature dehumidification efficiency of the evaporator, the evaporation temperature fluctuation is suppressed through the real-time adaptation of the compressor rotational speed, solving the technical problem of mutual interference in the temperature control of the evaporator and the heat exchanger in the traditional system.

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

[0021] Determine whether the current opening degree of the first expansion valve is within the corresponding opening degree range according to the opening degree of the second expansion valve and the corresponding relationship of the linkage opening degree;

[0022] If not, adjust the current opening degree to the upper limit or the lower limit of the closest opening degree range according to the relative size relationship between the current opening degree and the opening degree range;

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

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

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

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

[0027] In this embodiment, the first expansion valve is adjusted in an interval opening degree based on the preset corresponding relationship of the linkage opening degree. By preferentially aligning the boundary values of the opening degree range and combining step-by-step fine adjustment, the rapid matching of the refrigerant distribution of the double expansion valves is realized. This strategy avoids the refrigerant flow conflict in the double-valve adjustment process by forcing the alignment of the opening degree range boundary values. At the same time, combined with the hierarchical feedback adjustment of the evaporation target temperature difference, the evaporation temperature stabilization time is significantly shortened, and the robustness of the system under variable working conditions is enhanced.

[0028] Optionally, determining the rotational speed of the compressor according to the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature specifically includes:

[0029] Calculating a PI adjustment value of the compressor rotational speed based on the evaporation target temperature difference;

[0030] Generating a target rotational speed of the compressor according to the PI adjustment value, and determining whether the target rotational speed exceeds a preset rotational speed upper limit or a preset rotational speed lower limit corresponding to the current wind gear;

[0031] If not exceeding, adjusting the compressor rotational speed to the target rotational speed;

[0032] If exceeding, limiting the compressor rotational speed to the preset rotational speed upper limit;

[0033] If the target rotational speed is lower than the preset rotational speed lower limit, limiting the compressor rotational speed to the preset rotational speed lower limit;

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

[0035] In this embodiment, by combining the compressor rotational speed control with the PI adjustment algorithm and the wind gear rotational speed upper limit constraint, during the evaporation temperature adjustment process, the evaporation demand is adaptively adjusted by the compressor rotational speed first, and at the same time, the influence of the rotational speed sudden increase on the system stability is limited based on the wind gear level. This design not only ensures the dynamic response ability of the evaporation temperature control, but also avoids the overloading operation of the compressor through the rotational speed limiting mechanism, reducing the mechanical loss and noise problems caused by high-frequency start and stop.

[0036] Optionally, the method further includes:

[0037] Obtaining the current air-conditioning wind gear level, and obtaining the corresponding maximum allowable rotational speed of the compressor from a preset wind gear rotational speed mapping relationship;

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

[0039] If the duration of the compressor continuously running at the maximum allowable rotational speed exceeds a preset threshold, triggering a load reduction control; wherein, the triggering of the load reduction control includes increasing or decreasing the target air outlet temperature, or switching to a low wind gear operation mode.

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

[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 a second preset temperature;

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

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

[0045] In this embodiment, by limiting the boundary range of the preset operating temperature range and the target evaporation temperature range, the system can automatically adapt to the optimal evaporation temperature control threshold at a typical ambient temperature. This interval design takes into account both the dehumidification efficiency in a low-temperature environment and the system stability in a high-temperature environment, and avoids the risk of evaporator frosting or overheating due to insufficient environmental adaptability in traditional fixed threshold control.

[0046] Optionally, the method further includes:

[0047] Monitor the humidity in the car in real time and determine 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 air outlet temperature is reduced by a first correction value and the air outlet volume is reduced by a second correction value;

[0049] 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;

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

[0051] This embodiment realizes coordinated control of temperature and humidity by real-time monitoring of the humidity in the car and linkage correction of the target air outlet temperature and air volume parameters. The design dynamically adjusts the air outlet temperature setting value based on the humidity deviation, and combines the air volume correction to compensate for the impact of humidity changes on the perceived comfort. At the same time, the correction coefficient is optimized by the historical dehumidification frequency and the number of people in the car, so that the system can adapt to the personalized needs of different occupant scenarios, improving the intelligent 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] 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 execute a vehicle air-conditioning control method as described in any one of the above.

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

[0057] The above description is only an overview of the technical solution of the present disclosure. In order to be able to understand the technical means of the present disclosure more clearly, it can be implemented in accordance with the content of the specification. And in order to make the above and other objects, features and advantages of the present disclosure more obvious and understandable, the following specifically illustrates the specific embodiments of the present disclosure. Description of the Drawings

[0058] By reading the following detailed description of the preferred embodiments, various other advantages and benefits will become clear to those of ordinary skill in the art. The drawings are only for the purpose of showing the preferred embodiments and are not considered to be a limitation of the present disclosure. Moreover, throughout the drawings, the same reference numerals are used to represent the same components. In the drawings:

[0059] Figure 1 FIG. is a structural diagram of a vehicle air-conditioning control system provided by an embodiment of the present application;

[0060] Figure 2 FIG. is a flowchart of a vehicle air-conditioning control method provided by the present application;

[0061] Figure 3 FIG. is a schematic diagram of a control system of evaporation temperature - outlet air temperature provided by the present application;

[0062] Figure 4 FIG. is a schematic internal structure diagram of an electronic device provided by an embodiment of the present application.

[0063] Description of the Reference Numerals:

[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 Embodiments

[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 of this application and the corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of this application, rather than all the embodiments. Based on the embodiments in this application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the scope of protection of this application.

[0066] With the continuous improvement of the requirements for the energy efficiency and comfort of the air-conditioning system in new energy vehicles, the problem of insufficient adaptability of traditional air-conditioning control schemes under complex working conditions has become increasingly prominent. In the prior art, single-cool air-conditioning systems rely on PTC auxiliary heating devices for temperature compensation, resulting in a significant increase in energy consumption; although heat pump systems can improve the heating efficiency, they face conflicts in switching between the refrigeration mode and the heating mode under dehumidification working conditions and are difficult to simultaneously meet the requirements of low-temperature dehumidification and comfortable air outlet temperature. More critically, existing control strategies mostly adopt fixed-threshold regulation or single expansion valve control, unable to achieve dynamic coordination of the evaporation temperature, air outlet temperature, and compressor speed, resulting in poor system stability and low energy efficiency.

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

[0068] 1. Imbalance between energy efficiency and comfort: The temperature control method relying on PTC heating causes energy waste, and the lack of linkage between the compressor start-stop logic and the expansion valve regulation results in the coexistence of fluctuations in the evaporator temperature and overshoot of the air outlet temperature, making it impossible to balance energy efficiency and body sensation comfort during low-temperature dehumidification.

[0069] 2. Simplification of control dimensions: Existing systems mostly perform independent regulation based on a single parameter (such as the evaporation temperature or the air outlet temperature), and no dynamic mapping relationship is established among the opening degrees of the double expansion valves, the compressor speed, and the ambient temperature, resulting in mismatched refrigerant distribution and low heat exchange efficiency.

[0070] 3. Defects in system stability: The control of the compressor speed is disconnected from the air volume regulation, and equipment oscillations or thermal runaway caused by excessive speed are likely to occur under extreme working conditions. In addition, the expansion valve regulation lacks step-by-step segmented control and holding time constraints, and frequent actions are likely to cause sudden changes in the refrigerant flow rate, further deteriorating the system stability.

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

[0072] To solve the above problems, this application provides a vehicle air-conditioning control system, as Figure 1As shown in the figure, 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. Among them, the two ends of the first expansion valve 6 are respectively connected to the cooling medium inlet of the evaporator 1 and the cooling medium outlet of the pipeline connecting the intermediate heat exchange device 5 to the outdoor heat exchanger, and the two ends of the second expansion valve 7 are respectively connected to the cooling medium inlet of the outdoor heat exchanger 4 and the cooling medium outlet of the indoor heat exchanger 3. The compressor 2 is arranged between the intermediate heat exchange device 5 and the indoor heat exchanger 3.

[0073] Based on the above application system, the present application provides a vehicle air conditioner control method, as Figure 2 shown Figure 2 is a flowchart of a vehicle air conditioner control method provided by an embodiment of the present application, specifically including the following steps:

[0074] Step 201: In response to an air conditioner start instruction, collect the outdoor ambient temperature and determine whether the outdoor ambient temperature is within a preset operating condition temperature range.

[0075] In this embodiment, the triggering methods of the air conditioner start instruction include, but are not limited to, control signals initiated by the user through the in-vehicle touch screen, physical buttons, or mobile terminal APP. When the system detects the air conditioner start instruction, it first collects the outdoor ambient temperature through an ambient temperature sensor arranged inside the front bumper of the vehicle or at the base of the rearview mirror. It should be noted that the installation position of the sensor needs to avoid the heat source radiation area of the engine compartment and has a design to prevent rain interference to ensure the accuracy of the collected data.

[0076] Exemplarily, the preset operating condition temperature range is the temperature range for the system to operate efficiently, with its lower limit set as the first preset temperature (optional range 6°C - 9°C) and the upper limit as the second preset temperature (optional range 20°C - 24°C). It can be understood that the setting of this range is based on the following technical considerations: when the ambient temperature is lower than the lower limit, the evaporator is prone to frosting due to too low evaporation temperature, resulting in a sharp drop in dehumidification efficiency; when the ambient temperature is higher than the upper limit, the PTC auxiliary heating has a significant reduction in energy efficiency due to too high condensation temperature. Specifically, the system compares the collected outdoor ambient temperature with the preset range through a look-up table method. If the temperature value is within the range, it is determined that the dual expansion valve collaborative control mode can be enabled; 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 condition temperature range are not fixed. Exemplarily, in the adaptation for high-altitude areas or special climate vehicles, the lower limit selectable range can be adjusted to 7°C - 8°C and the upper limit selectable range can be adjusted to 22°C - 23°C through a software configuration tool to match the local typical environmental conditions. In addition, a hysteresis control logic is introduced in the system determination process: when the ambient temperature gradually rises from below the lower limit to 7°C, the switch to the dual-valve mode is delayed by 30 seconds to avoid frequent mode switching caused by temperature fluctuations.

[0078] Specifically, in a scenario where the ambient temperature in winter is 5°C, the system determines that the outside temperature is lower than the lower limit of the preset range, automatically disables the dual-valve collaborative control and enables the PTC heating mode; in a scenario where the ambient temperature in summer is 25°C, the system closes the first expansion valve due to the temperature exceeding the upper limit, and only adjusts the temperature through the refrigeration cycle and the second expansion valve. This design ensures system safety under extreme operating conditions and avoids ineffective energy consumption through dynamic mode switching.

[0079] It can be understood that the determination of the preset operating condition temperature range is a prerequisite for subsequent dual-valve collaborative control. If this step is skipped and the temperature adjustment is directly entered, frosting of the evaporator or overload of the compressor may occur under inapplicable operating conditions. For example, when forcibly enabling the dual-valve mode at an ambient temperature of 3°C, the evaporator temperature may drop below -5°C, causing icing and blocking the refrigerant flow, thus failing to achieve the purpose of dehumidification. Therefore, this step provides a stable operating basis for the subsequent control logic through the threshold screening of the ambient temperature.

[0080] Step 202: If available, turn on the compressor and determine the target outlet air temperature of the indoor heat exchanger according to the temperature control information included in the air conditioner startup command.

[0081] In this embodiment, the temperature control information includes the specific temperature value set by the user (such as 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 relation table stored in the vehicle-mounted controller. Exemplarily, the "comfort mode" corresponds to a dynamic temperature offset strategy, while the "rapid cooling" corresponds to the maximum refrigeration power output mode.

[0082] It can be understood that the generation of the target outlet air temperature needs to take into account the influence of the ambient temperature and the subjective needs of the user. Specifically, the system achieves this through the following methods:

[0083] Mode parsing: If the user selects a preset mode, the system generates a target temperature reference value by looking up a table according to the current ambient temperature. For example, when the ambient temperature is 15°C, the target outlet air temperature reference value corresponding to the "comfort mode" is 20°C; when the ambient temperature rises to 25°C, the reference value is adjusted to 23°C to avoid the discomfort of direct cold air blowing.

[0084] Dynamic offset: Add the environmental temperature compensation amount on the basis of the reference value. Exemplarily, for every 1°C higher than the reference environmental temperature (such as 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 the perceived temperature through progressive temperature adjustment.

[0085] User setting adaptation: If the user directly enters a specific temperature value (such as 22°C), the system uses this value as the target outlet air temperature, but will perform a rationality check in combination with the environmental temperature.

[0086] It should be noted that the generation process of the target outlet air temperature introduces a fuzzy control algorithm. Exemplarily, the system uses the environmental temperature, historical operation 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 through the membership function. For example, when it is detected that the number of occupants in the vehicle ≥ 3, the system reduces the target temperature by 1°C to compensate for the influence of human body heat dissipation.

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

[0088] It can be understood that the dynamic generation mechanism of the target outlet air temperature is the basis for the coordinated control of the two valves. If a fixed temperature setting value is used, when the environmental temperature fluctuates, it will cause the second expansion valve to be adjusted frequently and significantly, exacerbating system oscillation. For example, in areas with large temperature differences between day and night, when the environmental temperature drops at night, the dynamic target temperature automatically increases by 2°C, reducing the cooling demand and energy consumption, while maintaining the consistency of the perceived comfort.

[0089] Exemplarily, in spring when the environmental temperature is 18°C and the user selects the "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 stepwise reduce the target temperature in three times within 10 minutes (22°C → 21°C → 20°C), with an adjustment interval of 3 minutes each time. This progressive adjustment strategy can not only respond to the user's needs but also avoid the evaporation temperature fluctuation caused by sudden changes in the refrigerant flow rate.

[0090] In addition, the system learns the user's preferences through historical data. For example, if the user frequently manually sets the target temperature to 24°C when the environmental temperature is 25°C, the system will automatically adjust the reference value of the "comfort mode" from 23°C to 24°C under similar working conditions to achieve personalized adaptation. This design significantly improves the user experience by integrating preset logic and adaptive learning.

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

[0092] In a possible implementation manner of the present application, the opening degree of the second expansion valve is determined according to the actual air outlet temperature and the target air outlet temperature, which specifically includes: calculating the target temperature difference of the air outlet according to the actual air outlet temperature and the target air outlet temperature, and determining whether the target temperature difference of the air outlet is within a preset stable range of the air outlet temperature; if not, determining the opening degree adjustment step of the second expansion valve according to the corresponding relationship between the target temperature difference of the air outlet 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 maintaining the adjusted opening degree for a first preset time interval, determining whether the current target temperature difference of the air outlet is within a preset stable range of the air outlet temperature; if not, continue to adjust the opening degree of the second expansion valve until the current target temperature difference of the air outlet is within a preset stable range of the air outlet temperature.

[0093] In this embodiment, the adjustment of the opening degree of the second expansion valve is the core execution link of the air outlet temperature control. 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, and the change of its opening degree directly affects the refrigerant flow rate flowing into the indoor heat exchanger, thereby changing the heat exchange efficiency and the air outlet temperature.

[0094] Exemplarily, the actual air outlet temperature is collected in real time by a temperature sensor arranged at the air outlet of the indoor heat exchanger, and the system calculates the difference between it and the target air outlet temperature (i.e., the target temperature difference of the air outlet). It can be understood that the positive and negative signs of the temperature difference represent the adjustment direction: when the actual temperature is lower than the target value, it is necessary to reduce the opening degree of the second expansion valve to reduce the refrigerant flow rate; otherwise, increase the opening degree.

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

[0096]

[0097] Table 1

[0098] In the embodiment of the present application, the step adjustment strategy is as follows:

[0099] 1. Fast adjustment for large temperature difference: When the absolute value of the target temperature difference of the air outlet exceeds 13°C, a large step (such as 200 steps) is used for rapid approximation.

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

[0101] 3. Fine control for small temperature difference: When the temperature difference is less than 5°C, a small step (such as 50 steps) is used for fine adjustment to avoid overshoot and oscillation.

[0102] It should be noted that after each opening adjustment, the system forces the current opening to be maintained for at least the first preset time interval (such as 30 seconds). This design is based on the inertial characteristics of the refrigerant flow change: 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, it may cause misjudgment due to sensor response delay or thermal inertia, thereby causing oscillating regulation.

[0103] Specifically, in the high-temperature and rapid cooling scenario in summer, the system detects that the target air outlet temperature difference is -10°C (the actual temperature is higher than the target value), and immediately increases the opening of the second expansion valve by 200 steps to increase the refrigerant flow rate to enhance the heat exchange efficiency; after maintaining it for 30 seconds, the temperature difference is re-detected. If the temperature difference is reduced to -5°C, it switches to a small step size of 50 steps and continues to adjust until the temperature difference enters the stable range of ±2°C.

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

[0105]

[0106] Table 2

[0107] It can be understood that the step size adjustment strategy is similar to Figure 1 When the opening of the second expansion valve increases, more refrigerant flows to the outdoor heat exchanger through the indoor heat exchanger. At this time, the refrigerant flow of the evaporator is adjusted through the linkage of the first expansion valve to avoid the evaporation temperature from getting out of control.

[0108] Embodiment 1:

[0109] In a possible implementation of the present application, the method also includes: obtaining a target evaporating temperature of the evaporator based on the dehumidification information contained in the air-conditioning start instruction; controlling the opening of the first expansion valve based on the target evaporating temperature and the opening of the second expansion valve, and obtaining the actual evaporator temperature to determine the speed of the compressor based on the evaporation target temperature difference between the actual evaporating temperature and the target evaporating temperature.

[0110] In a possible implementation manner of the present application, the opening degree of the first expansion valve is controlled according to the target evaporation temperature and the opening degree of the second expansion valve, which specifically includes: according to the opening degree of the second expansion valve, using a preset linkage opening degree table to determine whether the current opening degree of the first expansion valve is within the corresponding opening degree range; if not, according to the relative size relationship between the current opening degree and the opening degree range, adjust the current opening degree to the upper limit or lower limit of the closest opening degree range; determine whether the evaporation target temperature difference is within the preset evaporation temperature stability range; if not, adjust the opening degree of the first expansion valve according to a preset first adjustment step; after maintaining the adjusted opening degree for a second preset time interval, determine whether the current evaporation target temperature difference is within the preset evaporation temperature stability range; if not, continue to adjust the opening degree of the first expansion valve according to the preset first adjustment step until the current evaporation target temperature difference is within the preset evaporation temperature stability range.

[0111] In a possible implementation manner of the present application, the rotation speed of the compressor is determined according to the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature, which specifically includes: based on the evaporation target temperature difference, calculating the PI adjustment value of the compressor rotation speed; generating a compressor target rotation speed according to the PI adjustment value, and determining whether the target rotation speed exceeds the preset rotation speed upper limit or rotation speed lower limit corresponding to the current wind gear; if not, adjusting the compressor rotation speed to the target rotation speed; if it exceeds, limiting the compressor rotation speed to the preset rotation speed upper limit; if the target rotation speed is lower than the preset rotation speed lower limit, limiting the compressor rotation speed to the preset rotation speed lower limit; when the evaporation target temperature difference is within the preset evaporation temperature stability range, maintaining the current compressor rotation speed until the temperature difference exceeds the stability range.

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

[0113] It can be understood that the dynamic range design of the target evaporation temperature solves the contradiction between low-temperature frosting and high-temperature efficiency decline in traditional fixed-threshold control. It should also be noted that an anti-oscillation protection mechanism can be introduced into the generation process of the target evaporation temperature of the present application. Exemplarily, when the ambient temperature fluctuates near the boundary of the preset working condition range (such as 19°C - 21°C), the system adopts a hysteresis control logic: if the temperature rises from 19°C to 20°C, delay for 1 minute before switching the target evaporation temperature range to avoid frequent adjustment caused by short-term temperature fluctuations.

[0114] It can be understood that if the dynamic setting of the target evaporation temperature is skipped and a fixed value is adopted, it is easy to cause system imbalance under variable working conditions. Therefore, this step provides an accurate adjustment reference for the subsequent dual-valve linkage and compressor speed control through the dynamic mapping relationship between the ambient temperature and the target evaporation temperature.

[0115] In this embodiment, the opening adjustment of the first expansion valve is strongly coupled with the state of the second expansion valve. The core lies in achieving the dynamic balance of stable evaporation temperature and outlet air temperature control through refrigerant distribution coordination. It should be noted that both ends of the first expansion valve are respectively connected to the cooling medium inlet of the evaporator and the outlet pipeline of the intermediate heat exchange device, and its opening change directly affects the refrigerant flow rate and evaporation pressure of the evaporator.

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

[0117] Exemplarily, the linkage opening table is as shown in Table 3 below:

[0118]

[0119] Table 3

[0120] In this embodiment, after the opening is aligned with the interval boundary, the system performs step-by-step adjustment according to the deviation between the actual temperature and the target temperature of the evaporator (evaporation target temperature difference). For example, if the actual evaporation temperature is 1.5 °C lower than the target value, the opening of the first expansion valve is gradually reduced at a step size of 10 steps per time, and the temperature response is observed by maintaining for 20 seconds (the second preset time interval) after each adjustment.

[0121] It can be understood that the essence of the linkage opening table is to establish a non-linear mapping relationship between the openings of the two valves. As Figure 2 shown, when the opening of the second expansion valve increases (increasing the refrigerant flow rate of the indoor heat exchanger), the opening of the first expansion valve needs to be synchronously reduced by 6 degrees, thereby restricting the flow rate of the evaporator and preventing the outlet air temperature from getting out of control due to excessive refrigerant distribution to the evaporator. For example, in the "rapid cooling" mode, the opening of the second expansion valve is increased to 800 steps to maximize the refrigeration power of the indoor heat exchanger. At this time, the opening of the first expansion valve is restricted to less than 300 steps to ensure that the evaporation temperature of the evaporator is not lower than the frosting threshold.

[0122] Exemplarily, in a dehumidification scenario where the ambient temperature is 10°C, the system sets the target temperature of the evaporator to 3°C. When the actual evaporation temperature is detected as 5°C (2°C higher than the target value), the system gradually reduces the opening of the first expansion valve in steps of 20 steps per time until the evaporation temperature drops to the stable range of 3°C ± 0.5°C. At the same time, the rotational speed of the compressor is adjusted in real time through the PI algorithm. For example, for every 1°C increase in the evaporation target temperature difference, the rotational speed of the compressor increases by 200 rpm, but it is limited by the current wind speed level. Table 4 below shows the maximum rotational speed of the compressor corresponding to the wind speed levels.

[0123]

[0124] Table 4

[0125] It should be noted that the wind speed - rotational speed coupling mechanism is introduced for the control of the compressor rotational speed. Exemplarily, in the low wind speed (1st gear) mode, the upper limit of the compressor rotational speed is 1500 rpm. At this time, if the target rotational speed calculated by the PI algorithm is 1800 rpm, the system will limit the actual rotational speed to 1500 rpm and trigger the load reduction control. This design combines the user operation intention (wind speed selection) with the equipment protection logic to avoid problems such as airflow noise or vibration caused by high rotational speed of the compressor under low air volume conditions.

[0126] In addition, the system dynamically switches the control mode through the determination of the stable range of the evaporation temperature (such as ±1°C). When the evaporation target temperature difference enters the stable range, the current rotational speed of the compressor is maintained until the temperature difference exceeds the threshold; if the temperature difference continuously exceeds 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. At this time, the system preferentially adjusts the rotational speed of the compressor (rather than frequently adjusting the first expansion valve) to quickly converge the temperature difference.

[0127] It can be understood that if the first expansion valve is independently adjusted while ignoring the double - valve linkage, it will lead to refrigerant distribution conflicts. For example, when the opening of the second expansion valve increases significantly, if the opening of the first expansion valve is not synchronously reduced, the excessive refrigerant flowing into the evaporator will cause the evaporation temperature to drop suddenly, which may further lead to the risk of frosting or liquid slugging of the compressor. Therefore, in this step, a control system for evaporation temperature - outlet air temperature is constructed, as Figure 3 shown. It should be noted that Figure 3 EXV1 and EXV2 in

[0128] Example 2:

[0129] In a possible implementation manner of the present application, the method further includes: obtaining the current air conditioner wind gear level, and obtaining the corresponding maximum allowable speed of the compressor from a preset wind gear 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 duration of the compressor continuously running at the maximum allowable speed exceeds a preset threshold, triggering a load reduction control; wherein, triggering the load reduction control includes increasing or decreasing the target air outlet temperature, and switching to a low wind gear operation mode.

[0130] In this embodiment, the wind gear level is set through a user operation interface (such as a physical knob or a touch screen), and its value (such as 1-3 gears) is mapped to the upper limit of the compressor speed. It should be noted that the wind gear - speed mapping relationship is designed based on the balance between the air volume demand and noise control: the low wind gear (such as gear 1) corresponds to a low speed to reduce the air flow noise, and the high wind gear (such as gear 3) allows a higher speed to meet the rapid temperature control demand.

[0131] Exemplarily, as Figure 2 shown, the compressor is located on the main circulation path between the intermediate heat exchange device and the indoor heat exchanger. Its speed directly affects the flow distribution of the refrigerant flowing from the indoor heat exchanger to the outdoor heat exchanger and the evaporator. Specifically, the system looks up the table according to the current wind gear level to obtain the maximum allowable speed of the compressor: gear 1 (low air volume): the upper limit of the speed is 1500 rpm, which is applicable to the scenario where silence is prioritized (such as night driving); gear 2 (medium air volume): the upper limit of the speed is 2000 rpm, balancing the cooling speed and energy consumption; gear 3 (high air volume): the upper limit of the speed is 2500 rpm, which is used for rapid cooling or extremely humid and hot environments.

[0132] It can be understood that the speed limiting mechanism is closely related to the physical position of the compressor. When the compressor speed increases, the flow rate of the refrigerant from the indoor heat exchanger through the indoor heat exchanger speeds up. At this time, the opening of the second expansion valve needs to be adjusted to match the flow rate to avoid the out-of-control of the evaporator temperature caused by pressure mutation. For example, at the air volume of gear 3, if the compressor runs at 2500 rpm, the opening of the second expansion valve 7 needs to be increased to 800 steps synchronously to maintain the stability of the air outlet temperature.

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

[0134] Embodiment Three:

[0135] In a possible implementation manner of the present 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 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 volume is increased by a fourth correction value; the first correction value and the second correction value are determined based on the historical frequency of turning on the dehumidification mode of the vehicle and / or the number of people inside the vehicle.

[0136] It should be noted that since in the dehumidification mode, reducing the air volume can increase 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 dehumidification effect is enhanced by reducing the air volume, and when the current humidity is lower than the lower limit of the comfortable humidity range, the dehumidification effect is reduced by increasing the air volume. In addition, since reducing the target air outlet temperature will synchronously reduce the temperature of the evaporator, 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 air outlet temperature is synchronously reduced by a first correction value, and when the current humidity is lower than the lower limit of the comfortable humidity range, the target air outlet temperature is synchronously increased by a third correction value.

[0137] In this embodiment, the real-time humidity data is collected by a humidity sensor arranged on the vehicle ceiling or under the seat, and the comfortable humidity range is set to 40%-60%. When the humidity is higher than the upper limit, the system reduces the target air outlet temperature by 1°C - 2°C and reduces the air volume by 10% - 20% to relieve the stuffy feeling caused by high humidity; when the humidity is lower than the lower limit, the target air outlet temperature and the air volume are adjusted in the reverse direction. The correction value is dynamically adjusted according to the historical dehumidification frequency and the number of people in the vehicle: if the vehicle has frequently enabled the dehumidification function recently or the number of passengers ≥ 3, the temperature correction range increases by 0.5°C - 1°C, and the air volume correction ratio increases by 5% - 10%. For example, in the plum rain season, when the system detects that the average daily dehumidification duration in the past week exceeds 2 hours, the temperature correction value when the humidity exceeds the limit is automatically adjusted from 1°C to 1.5°C to enhance the dehumidification response.

[0138] Embodiment 4:

[0139] In this embodiment, the compressor speed can be controlled by looking up a table according to the blower air volume, ambient temperature, internal and external circulation ratio, or the air inlet temperature in front of the evaporator, etc., and restrictions should be imposed.

[0140] In this embodiment, the control architecture is as Figure 1 shown. The intermediate heat exchange device can be removed, or replaced by a liquid storage tank and a coaxial tube, which can be regarded as a deformation of the corresponding architecture of this control algorithm, and restrictions should also be imposed.

[0141] In this embodiment, the interlock control of the first expansion valve and the second expansion valve does not necessarily rely on Table 2. Instead, it can be achieved through the opening degrees of the first expansion valve and the second expansion valve, and restrictions should also be imposed in the same way.

[0142] The above is the method embodiment proposed by this application. Based on the same inventive concept, this application embodiment also provides an electronic device, the structure of which is as Figure 4 shown.

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

[0144] At least one processor 401;

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

[0146] Wherein, the memory 402 stores instructions executable by the at least one processor. The instructions are executed by the at least one processor 401 so that the at least one processor 401 can:

[0147] In response to an air conditioner start instruction, collect the outdoor ambient temperature and determine whether the outdoor ambient temperature is within a preset operating condition temperature range;

[0148] If so, start the compressor and determine the target outlet air temperature of the indoor heat exchanger according to the temperature control information included in the air conditioner start instruction;

[0149] Determine the opening degree of the second expansion valve according to the actual outlet air temperature and the target outlet air temperature to achieve control of the outlet air temperature.

[0150] Some embodiments of this application provide a Figure 1 corresponding computer-readable storage medium storing computer-executable instructions, and the computer-executable instructions are set to:

[0151] In response to an air conditioner start instruction, collect the outdoor ambient temperature and determine whether the outdoor ambient temperature is within a preset operating condition temperature range;

[0152] If so, start the compressor and determine the target outlet air temperature of the indoor heat exchanger according to the temperature control information included in the air conditioner start instruction;

[0153] Determine the opening degree of the second expansion valve according to the actual outlet air temperature and the target outlet air temperature to achieve control of the outlet air temperature.

[0154] Each embodiment in this application is described in a progressive manner. For the same or similar parts among the embodiments, reference can be made to each other, and the key points of each embodiment are the differences from other embodiments. In particular, for the embodiments of the Internet of Things devices and media, since they are basically similar to the method embodiments, the description is relatively simple, and reference can be made to the corresponding parts of the method embodiments for relevant details.

[0155] The systems and media provided by the embodiments of this application correspond one by one to the methods. Therefore, the systems and media also have beneficial technical effects similar to those of 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 elaborated here.

[0156] Those skilled in the art should understand that the embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a complete hardware embodiment, a complete software embodiment, or an embodiment combining software and hardware aspects. Moreover, this application can take the form of a computer program product implemented on one or more computer-usable storage media (including but not limited to disk memories, CD-ROMs, optical memories, etc.) that contain computer-usable program code.

[0157] This application is described with reference to the flowcharts and / or block diagrams of methods, devices (systems), and computer program products according to the embodiments of this application. It should be understood that each flow and / or block in the flowchart and / or block diagram can be implemented by computer program instructions, and the combination of the flows and / or blocks in the flowchart and / or block diagram can also be implemented by computer program instructions. These computer program instructions can be provided to the processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing devices to generate a machine, so that the instructions executed by the processor of the computer or other programmable data processing devices generate a device for implementing the functions specified in Figure 1 one or more of the flows Figure 1 or a combination of multiple flows and / or blocks

[0158] These computer program instructions can also be stored in a computer-readable memory that can direct a computer or other programmable data processing device to work in a specific manner, so that the instructions stored in the computer-readable memory generate a manufactured article including an instruction device, and the instruction device implements the functions specified in Figure 1 one or more of the flows Figure 1 or a combination of multiple flows and / or blocks

[0159] These computer program instructions can also be loaded onto a computer or other programmable data processing apparatus, causing a series of operational steps to be performed on the computer or other programmable apparatus to generate a computer-implemented process, so that the instructions executed on the computer or other programmable apparatus provide steps for implementing the functions specified in one process Figure 1 one process or a plurality of processes and / or blocks Figure 1 steps of the functions specified in one block or a plurality of blocks.

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

[0161] The memory may include non-permanent memory in the form of computer-readable media, random access memory (RAM) and / or non-volatile memory such as read-only memory (ROM) or flash memory (flash RAM). The memory is an example of computer-readable media.

[0162] Computer-readable media includes both permanent and non-permanent, removable and non-removable media implemented by any method or technology for storing information. The information can be computer-readable instructions, data structures, program modules, 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, compact disc read-only memory (CD-ROM), digital versatile discs (DVD) or other optical storage, magnetic cassettes, magnetic tape magnetic disk storage or other magnetic storage devices, or any other non-transmission media that can be used to store information that can be accessed by a computing device. As defined herein, computer-readable media does not include transitory media such as modulated data signals and carrier waves.

[0163] It should also be noted that the term "comprising", "including" or any other variation thereof is intended to cover non-exclusive inclusion, so that a process, method, commodity or device comprising a series of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, commodity or device. Without further limitation, an element defined by the statement "comprising a..." does not exclude the presence of additional identical elements in the process, method, commodity or device comprising the element.

[0164] The above are only embodiments of the present application and are not intended to limit the present application. For those skilled in the art, various changes and modifications can be made to the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included within the scope of the claims of the present application.

Claims

1. A vehicle air conditioning control method, characterized in that: Applied to a vehicle air conditioning control system, the system includes: an evaporator, a compressor, an indoor heat exchanger, an outdoor heat exchanger, a first expansion valve, and a second expansion valve, 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 connected to the outdoor heat exchanger pipeline, 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 method includes: In response to an air-conditioning start instruction, collecting the ambient temperature outside the vehicle, and determining whether the ambient temperature outside the vehicle is within a preset operating temperature range; If yes, start the compressor, and determine the target air outlet temperature of the indoor heat exchanger according to the temperature control information contained in the air conditioner start instruction; The opening degree of the second expansion valve is determined according to the actual air outlet temperature and the target air outlet temperature to achieve control of the air outlet temperature.

2. The vehicle air conditioning control method according to claim 1, characterized in that: The determining the opening degree of the second expansion valve according to the actual air outlet temperature and the target air outlet temperature specifically includes: Calculating a target air outlet temperature difference according to the actual air outlet temperature and the target air outlet temperature, and determining whether the target air outlet temperature difference is within a preset air outlet temperature stability range; If not, determining the opening adjustment step of the second expansion valve according to the correspondence between the air outlet target temperature difference 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; After the adjusted opening is maintained for a first preset time interval, determining whether the current air outlet target temperature difference is within a preset air outlet temperature stability range; If not, continue to adjust the opening of the second expansion valve until the current air outlet target temperature difference is within the preset air outlet temperature stable range.

3. The vehicle air conditioning control method according to claim 1, characterized in that: The method further comprises: Obtaining a target evaporation temperature of the evaporator according to the dehumidification information contained in the air-conditioning start instruction; According to the target evaporation temperature and the opening of the second expansion valve, the opening of the first expansion valve is controlled, and the actual evaporator temperature is obtained to determine the rotation speed of the compressor according to the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature.

4. The vehicle air conditioning control method according to claim 3, characterized in that: The controlling the opening of the first expansion valve according to the target evaporation temperature and the opening of the second expansion valve specifically includes: According to the corresponding relationship between the opening degree of the second expansion valve and the linkage opening degree, determining whether the current opening degree of the first expansion valve is within the corresponding opening degree range; If not, adjusting the current opening to the closest upper limit or lower limit of the opening interval according to the relative size relationship between the current opening and the opening interval; Determining whether the evaporation target temperature difference is within a preset evaporation temperature stable range; If not, adjusting the opening of the first expansion valve according to a preset first adjustment step; After maintaining the adjusted opening for a second preset time interval, determining whether the current evaporation target temperature difference is within a preset evaporation temperature stable range; If not, continue to adjust the opening of the first expansion valve according to the preset first adjustment step until the current evaporation target temperature difference is within the preset evaporation temperature stable range.

5. The vehicle air conditioning control method according to claim 3, characterized in that: The step of determining the rotation speed of the compressor according to the evaporation target temperature difference between the actual evaporation temperature and the target evaporation temperature specifically includes: Calculating a PI adjustment value of the compressor speed based on the evaporation target temperature difference; Generate a compressor target speed according to the PI adjustment value, and determine whether the target speed exceeds a preset upper speed limit or a preset lower speed limit corresponding to the current wind speed; If not, adjusting the compressor speed to the target speed; If exceeded, the compressor speed is limited to the preset upper speed limit; If the target speed is lower than the preset speed lower limit, limiting the compressor speed to the preset speed lower limit; When the evaporation target temperature difference is within a preset evaporation temperature stable range, the current compressor speed is maintained until the temperature difference exceeds the stable range.

6. The vehicle air conditioning control method according to claim 1, characterized in that: The method further comprises: Get the current air conditioner wind speed level, and get the corresponding maximum allowable compressor speed from the preset wind speed mapping relationship; 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 continuously runs at the maximum allowable speed for a period exceeding a preset threshold, load reduction control is triggered; wherein, the triggering of load reduction control includes increasing or decreasing the target air outlet temperature and switching to a low wind speed operation mode.

7. The vehicle air conditioning control method according to claim 3, characterized in that: The lower limit of the preset operating temperature range is a first preset temperature; The upper limit of the preset operating temperature range is a second preset temperature; The lower limit of the temperature range of the target evaporation temperature is a third preset temperature; The upper limit of the temperature range of the target evaporation temperature is a fourth preset temperature.

8. The vehicle air conditioning control method according to claim 1, characterized in that: The method further comprises: Monitor the humidity in the car in real time and determine 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 starting the dehumidification mode in the history of the vehicle and / or the number of people in the vehicle.

9. An electronic device, characterized in that: The device comprises: at least one processor; and, a memory communicatively coupled to the at least one processor; The memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor so that the at least one processor can execute a vehicle air conditioning control method as described in any one of claims 1-8.

10. A vehicle, characterized in that: The vehicle comprises: A memory for storing executable program codes; A processor, configured to call and run the executable program code from the memory so that the vehicle executes the method according to any one of claims 1 to 8.

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