Control method and device for vehicle compressor, vehicle and medium

Abstract

The invention provides a control method and device for a vehicle compressor, a vehicle and a medium. The vehicle further comprises an air blower, an evaporator and a compressor, the evaporator and the compressor are connected through a refrigerant pipeline provided with a refrigerant pressure sensor, and the method comprises the steps that in response to a temperature adjusting instruction sent by a user, the target temperature of the evaporator is obtained, and the reference rotating speed of the evaporator is determined according to the target temperature of the evaporator and the actual temperature of the evaporator; in a pre-calibrated refrigerant pressure gauge, a refrigerant target pressure value is searched according to the voltage of an air blower and the air inlet temperature of an evaporator, and the refrigerant pressure reference rotating speed is determined according to the refrigerant target pressure value and the refrigerant actual pressure value; a target compressor speed is selected from the evaporator reference speed and the refrigerant pressure reference speed to control the compressor. Excessive dependence on the temperature sensor is avoided, the more accurate rotating speed of the compressor can be obtained so as to improve the control precision, and the stability and reliability of operation of the vehicle air conditioning system are guaranteed.

Description

Technical Field

[0001] This application relates to the field of compressor control, and in particular to a control method, device, vehicle, and medium for a vehicle compressor. Background Technology

[0002] In vehicle air conditioning systems, compressor speed control primarily depends on evaporator temperature. Typically, the required compressor speed can be calculated by comparing the difference between the actual evaporator temperature and the target temperature.

[0003] However, if the evaporator temperature sensor is not installed correctly or malfunctions, or if there is a signal delay in the sensor, there may be a significant difference between the detected evaporator temperature and the actual temperature. In this case, the compressor speed determined based on the detected evaporator temperature may be incorrect, or even impossible to obtain. Relying on inaccurate compressor speed to control the compressor will lead to reduced compressor control precision, thereby affecting the stability and reliability of the vehicle's air conditioning system. Summary of the Invention

[0004] In view of the above problems, this application proposes a control method, device, vehicle, and medium for a vehicle compressor.

[0005] In a first aspect of this application, a method for controlling a vehicle compressor is provided. The vehicle further includes a blower, an evaporator, and a compressor. The evaporator and the compressor are connected via a refrigerant pipeline, and a refrigerant pressure sensor is installed in the refrigerant pipeline. The method includes: In response to a temperature adjustment command issued by the user, the target evaporator temperature corresponding to the temperature adjustment command is obtained; The actual temperature of the evaporator is collected, and the reference rotation speed of the evaporator is determined based on the target temperature and the actual temperature of the evaporator. Obtain the blower voltage of the blower and collect the evaporator inlet air temperature of the evaporator; The target refrigerant pressure value is obtained by finding the blower voltage and the evaporator inlet air temperature in a pre-calibrated refrigerant pressure gauge. The refrigerant pressure sensor is used to collect the actual refrigerant pressure value, and the refrigerant pressure reference rotation speed is determined based on the target refrigerant pressure value and the actual refrigerant pressure value. The target compressor speed is selected from the evaporator reference speed and the refrigerant pressure reference speed, and the compressor is controlled using the target compressor speed.

[0006] Optionally, the vehicle further includes an evaporator temperature sensor, wherein acquiring the actual evaporator temperature and determining the evaporator reference rotation speed based on the target evaporator temperature and the actual evaporator temperature includes: The actual temperature of the evaporator is collected using the evaporator temperature sensor. The evaporator temperature difference is determined based on the target evaporator temperature and the actual evaporator temperature. Obtain the preset initial compressor speed, and determine the evaporator reference speed based on the initial compressor speed and the temperature difference of the evaporator.

[0007] Optionally, the step of using the refrigerant pressure sensor to collect the actual refrigerant pressure value and determining the refrigerant pressure reference rotation speed based on the target refrigerant pressure value and the actual refrigerant pressure value includes: The actual refrigerant pressure value is collected using the aforementioned refrigerant pressure sensor; The refrigerant pressure difference is determined based on the target refrigerant pressure value and the actual refrigerant pressure value. Obtain the preset initial compressor speed, and determine the refrigerant pressure reference speed based on the initial compressor speed and the refrigerant pressure difference.

[0008] Optionally, selecting the target compressor speed from the evaporator reference speed and the refrigerant pressure reference speed, and controlling the compressor using the target compressor speed, includes: If the evaporator reference speed is greater than the refrigerant pressure reference speed, then the refrigerant pressure reference speed is used as the target compressor speed, and the compressor is controlled using the target compressor speed; If the evaporator reference speed is less than the refrigerant pressure reference speed, then the evaporator reference speed is used as the target compressor speed, and the compressor is controlled using the target compressor speed; If the evaporator reference speed is equal to the refrigerant pressure reference speed, then the evaporator reference speed or the refrigerant pressure reference speed is taken as the target compressor speed, and the compressor is controlled using the target compressor speed.

[0009] Optionally, the refrigerant pressure gauge is calibrated in the following manner: Obtain several preset evaporator inlet air temperatures and several preset evaporator inlet air volumes; In the preset vehicle simulation model, the target refrigerant pressure value is obtained by simulating based on any of the evaporator inlet air temperature and any of the evaporator inlet air volume. An initial refrigerant pressure gauge is constructed based on the evaporator inlet air temperature, the evaporator inlet air volume, and the refrigerant target pressure value. In actual vehicles, the blower voltage corresponding to any of the evaporator intake air volumes is obtained by testing the evaporator intake air volume. In the initial refrigerant pressure gauge, for any evaporator inlet air volume, the blower voltage corresponding to the evaporator inlet air volume is used to replace the evaporator inlet air volume, resulting in a refrigerant pressure gauge composed of the evaporator inlet air temperature, the blower voltage, and the refrigerant target pressure value.

[0010] Optionally, the step of simulating in a preset vehicle simulation model based on any of the evaporator inlet air temperatures and any of the evaporator inlet air volumes to obtain the refrigerant target pressure value includes: Obtain the preset evaporator calibration temperature; In the preset vehicle simulation model, simulation is performed based on any of the evaporator inlet air temperatures and any of the evaporator inlet air volumes, and the evaporator reference temperature in the vehicle simulation model is collected. When the evaporator reference temperature is consistent with the evaporator calibration temperature, the refrigerant pressure value in the vehicle simulation model is used as the refrigerant target pressure value.

[0011] Optionally, the step of testing the evaporator intake airflow in an actual vehicle to obtain the blower voltage corresponding to the evaporator intake airflow includes: In actual vehicles, the air intake air volume of any of the evaporators is tested, and the measured air volume of the evaporators in the actual vehicles is collected. When the measured air volume of the evaporator is consistent with the air volume of the evaporator intake, the blower voltage in the actual vehicle is taken as the blower voltage corresponding to the air volume of the evaporator intake.

[0012] In a second aspect of this application, a control device for a vehicle compressor is also provided. The vehicle further includes a blower, an evaporator, and a compressor. The evaporator and the compressor are connected via a refrigerant line, and a refrigerant pressure sensor is disposed in the refrigerant line. The device includes: The target temperature acquisition module is used to acquire the target evaporator temperature corresponding to the temperature adjustment command issued by the user in response to the temperature adjustment command. The first speed determination module is used to collect the actual temperature of the evaporator and determine the reference speed of the evaporator based on the target temperature and the actual temperature of the evaporator. The voltage and temperature acquisition module is used to acquire the blower voltage of the blower and the evaporator inlet air temperature of the evaporator. The target pressure determination module is used to find the target refrigerant pressure value based on the blower voltage and the evaporator inlet air temperature in a pre-calibrated refrigerant pressure gauge. The second speed determination module is used to collect the actual pressure value of the refrigerant using the refrigerant pressure sensor, and determine the refrigerant pressure reference speed based on the target pressure value of the refrigerant and the actual pressure value of the refrigerant. The target speed determination module is used to select a target compressor speed from the evaporator reference speed and the refrigerant pressure reference speed, and to control the compressor using the target compressor speed.

[0013] In a third aspect of this application, a vehicle is also provided, including a processor, a memory, and a computer program stored in the memory and capable of running on the processor, wherein the computer program, when executed by the processor, implements the method described above.

[0014] In a fourth aspect of this application, a computer-readable storage medium is also provided, on which a computer program is stored, which, when executed by a processor, implements the method described above.

[0015] The embodiments of this application have the following advantages: In this embodiment, in response to a user-issued temperature adjustment command, the system obtains the target evaporator temperature corresponding to the command, collects the actual evaporator temperature, determines the evaporator reference speed based on the target and actual temperatures, obtains the blower voltage, and collects the evaporator inlet air temperature. In a pre-calibrated refrigerant pressure gauge, the system finds the target refrigerant pressure value based on the blower voltage and evaporator inlet air temperature. A refrigerant pressure sensor collects the actual refrigerant pressure value, and a refrigerant pressure reference speed is determined based on the target and actual pressure values. A target compressor speed is selected from the evaporator reference speed and the refrigerant pressure reference speed, and the compressor is controlled using the target compressor speed. The vehicle compressor control method provided in this embodiment first obtains the target evaporator temperature in response to a user-issued temperature adjustment command, allowing for adjustments based on the user's actual needs, thus improving user experience and comfort. Secondly, by determining the evaporator reference speed based on the target and actual temperatures, and by real-time monitoring of the actual evaporator temperature and comparing it with the target temperature, the compressor reference speed can be accurately calculated. Furthermore, by acquiring the blower voltage and collecting the evaporator inlet air temperature, multiple parameters are introduced, moving beyond reliance solely on evaporator temperature to improve the robustness of compressor speed control. Then, using a pre-calibrated refrigerant pressure gauge, the target refrigerant pressure value is determined based on the blower voltage and evaporator inlet air temperature. The actual refrigerant pressure value is collected using a refrigerant pressure sensor. A refrigerant pressure reference speed is determined based on the target and actual refrigerant pressure values. Even if the evaporator temperature sensor is not correctly installed or malfunctions, or if there is a signal delay, the target refrigerant pressure value can still be determined based on the blower voltage and evaporator inlet air temperature, thus establishing an accurate refrigerant pressure reference speed. Finally, the target compressor speed is selected from the evaporator reference speed and the refrigerant pressure reference speed, and the compressor is controlled using this target compressor speed. Selecting the target compressor speed from two reference speeds avoids the potential inaccuracy of compressor speed obtained through a single method, resulting in a more precise compressor speed, improving compressor control accuracy, and ultimately ensuring the stability and reliability of the vehicle's air conditioning system. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below.

[0017] Figure 1 This is a flowchart illustrating the steps of a vehicle compressor control method according to an embodiment of this application; Figure 2 This is a schematic diagram of components of a vehicle air conditioning system according to an embodiment of this application; Figure 3 This is a flowchart illustrating the steps of compressor control according to an embodiment of this application; Figure 4 This is a comparison diagram of the control effect of evaporator temperature provided in one embodiment of this application; Figure 5 This is a comparison diagram of the control effect of compressor speed according to an embodiment of this application; Figure 6 This is a schematic diagram of the structure of a vehicle compressor control device provided in one embodiment of this application. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the various embodiments of this application will be described in detail below with reference to the accompanying drawings. However, those skilled in the art will understand that many technical details have been presented in the various embodiments of this application to enable readers to better understand this application. However, the technical solutions claimed in this application can be implemented even without these technical details and various changes and updates based on the following embodiments. The division of the various embodiments below is for the convenience of description and should not constitute any limitation on the specific implementation of this application. The various embodiments can be combined with and referenced by each other without contradiction.

[0019] In related technologies, the control of compressor speed in vehicle air conditioning systems mainly depends on the evaporator temperature. Typically, the required compressor speed can be calculated by comparing the difference between the actual evaporator temperature and the target temperature.

[0020] During compressor temperature control, the temperature sensor has a slow response time and cannot quickly reflect the actual temperature of the evaporator. This results in a certain difference between the evaporator temperature collected by the sensor and the actual temperature of the evaporator. Consequently, the difference between the evaporator temperature collected by the sensor and the target temperature deviates significantly from the difference between the actual temperature of the evaporator and the target temperature.

[0021] This delay causes the compressor to run at high speed for extended periods. Taking the cooling process as an example, when the evaporator temperature sensor detects that the temperature has reached the target temperature, the actual evaporator temperature is already below the target. As time progresses, the temperature detected by the sensor gradually falls below the target temperature, causing the compressor to reduce its speed, which in turn leads to a rise in the actual evaporator temperature. When the sensor detects that the temperature has reached the target temperature again, the actual evaporator temperature is already above the target, and the sensor reading continues to rise, deviating from the target temperature, causing the compressor speed to increase again. This repeated fluctuation makes compressor speed control unstable until the sensor reading perfectly matches the actual temperature value, at which point the compressor speed can operate smoothly.

[0022] During this process, because the actual temperature of the evaporator is lower than the temperature collected by the sensor, frost may easily form on the evaporator.

[0023] On the other hand, if the evaporator temperature sensor is improperly assembled, such as not being correctly installed inside the HVAC (Heating, Ventilation, and Air Conditioning) system, the evaporator temperature collected by the sensor will be even lower than the actual evaporator temperature. This will cause the compressor to run at a high speed continuously, increasing the risk of evaporator frosting. Furthermore, if the evaporator temperature sensor malfunctions, the compressor will be unable to start the cooling function, further affecting the normal operation of the air conditioning system.

[0024] Therefore, this application provides a control method, device, vehicle, and medium for a vehicle compressor. In addition to using the evaporator temperature difference to control the compressor speed, it also introduces refrigerant pressure synchronization for compressor speed control. Even if the evaporator temperature sensor is not correctly installed or malfunctions, or if there is a signal delay from the sensor, the target refrigerant pressure value can be determined based on the blower voltage and evaporator inlet air temperature, thereby determining an accurate refrigerant pressure reference speed. This avoids the problem of potentially inaccurate compressor speed obtained through a single method, resulting in a more precise compressor speed, improved compressor control accuracy, and thus ensuring the stability and reliability of the vehicle's air conditioning system.

[0025] Reference Figure 1 The diagram shows a flowchart of the steps of a vehicle compressor control method according to an embodiment of this application.

[0026] In this embodiment, the vehicle compressor control method can be applied to a controller, which can be a core component of the vehicle air conditioning system and can be responsible for managing and coordinating the various components of the system to achieve precise temperature control and optimized system operation.

[0027] In this embodiment, the vehicle also includes a blower, an evaporator, and a compressor. The evaporator and compressor are connected via a refrigerant pipeline, and a refrigerant pressure sensor is installed in the refrigerant pipeline.

[0028] The blower can be used to draw air in from outside or inside the vehicle, cool or heat it through an evaporator, and then deliver the treated air into the vehicle. In this embodiment, the blower voltage can be used to represent the evaporator intake air volume.

[0029] An evaporator can refer to a heat exchanger in an air conditioning system, which absorbs heat through the evaporation of refrigerant, thereby cooling the air flowing through it. In this embodiment, the reference rotational speed of the evaporator can be obtained from its actual temperature.

[0030] The compressor is also a core component of the air conditioning system, responsible for compressing the refrigerant, increasing its pressure and temperature, and driving the refrigerant to circulate within the system. In this embodiment, the evaporator and compressor can be connected via refrigerant piping.

[0031] A refrigerant line can refer to a pipe connecting the evaporator and the compressor, and can be used to transport refrigerant. In the embodiments of this application, a refrigerant pressure sensor can be installed in the refrigerant line.

[0032] A refrigerant pressure sensor can be installed in the refrigerant pipeline to monitor the refrigerant pressure in real time, providing data support for compressor speed control. In this embodiment, the actual refrigerant pressure value can be acquired using the refrigerant pressure sensor.

[0033] The method may specifically include the following steps: Step 101: In response to the temperature adjustment command issued by the user, obtain the target temperature of the evaporator corresponding to the temperature adjustment command.

[0034] In this embodiment, in response to a temperature adjustment command issued by the user, the target evaporator temperature corresponding to the temperature adjustment command can be obtained. The target evaporator temperature can refer to the temperature set by the user, representing the temperature target the user expects the evaporator to reach.

[0035] Step 102: Collect the actual temperature of the evaporator and determine the reference rotation speed of the evaporator based on the target temperature and the actual temperature of the evaporator.

[0036] In this embodiment of the application, the actual temperature of the evaporator can be collected, and the reference rotation speed of the evaporator can be determined based on the target temperature and the actual temperature of the evaporator.

[0037] The actual evaporator temperature refers to the evaporator temperature obtained in real time by the evaporator temperature sensor; it is the actual evaporator temperature obtained at the sensor level. The evaporator reference speed is a compressor speed reference value calculated based on the temperature difference between the target evaporator temperature and the actual evaporator temperature.

[0038] Step 103: Obtain the blower voltage of the blower and collect the evaporator inlet air temperature of the evaporator.

[0039] In this embodiment, the blower voltage of the blower can be obtained, and the evaporator inlet air temperature can be collected. The blower voltage refers to the operating voltage of the blower, which reflects the blower's airflow and thus the airflow entering the evaporator. The evaporator inlet air temperature refers to the temperature of the air entering the evaporator.

[0040] In practice, both the airflow rate and the air temperature entering the evaporator affect its heat exchange performance, thus impacting the refrigerant pressure. For example, a higher airflow rate results in lower refrigerant pressure, while a lower airflow rate results in higher refrigerant pressure. Similarly, a higher air temperature results in higher refrigerant pressure, while a lower air temperature results in lower refrigerant pressure. These two parameters allow us to determine the corresponding refrigerant pressure values.

[0041] Step 104: In the pre-calibrated refrigerant pressure gauge, the target refrigerant pressure value is obtained based on the blower voltage and the evaporator inlet air temperature.

[0042] In this embodiment, the target refrigerant pressure value can be found in a pre-calibrated refrigerant pressure table based on the blower voltage and evaporator inlet air temperature. The refrigerant pressure table is a pre-calibrated table that records the target refrigerant pressure values ​​corresponding to different blower voltages and evaporator inlet air temperatures. The target refrigerant pressure value can be the refrigerant pressure value that, at a given blower voltage and evaporator inlet air temperature, causes the actual temperature of the evaporator body to reach the target evaporator temperature.

[0043] In practical implementation, the pre-calibrated refrigerant pressure gauge can be in the form shown in Table 1 below: Table 1 Refrigerant Pressure Gauge

[0044] Step 105: Use the refrigerant pressure sensor to collect the actual refrigerant pressure value, and determine the refrigerant pressure reference rotation speed based on the refrigerant target pressure value and the actual refrigerant pressure value.

[0045] In this embodiment, a refrigerant pressure sensor can be used to collect the actual refrigerant pressure value, and a refrigerant pressure reference speed can be determined based on the target refrigerant pressure value and the actual refrigerant pressure value. The actual refrigerant pressure value refers to the current actual refrigerant pressure collected in real time by the refrigerant pressure sensor. The refrigerant pressure reference speed refers to a compressor speed reference value calculated based on the pressure difference between the target refrigerant pressure value and the actual refrigerant pressure value.

[0046] Step 106: Select a target compressor speed from the evaporator reference speed and the refrigerant pressure reference speed, and control the compressor using the target compressor speed.

[0047] In this embodiment, a target compressor speed can be selected from the evaporator reference speed and the refrigerant pressure reference speed, and the compressor can be controlled using the target compressor speed. The target compressor speed refers to the finally determined compressor operating speed.

[0048] In practice, the smaller of the evaporator reference speed and the refrigerant pressure reference speed can be selected as the target compressor speed, and the compressor can be controlled using the target compressor speed. This avoids the compressor from continuously operating at a high speed, thereby preventing evaporator frosting.

[0049] In practical implementation, the component structure of the vehicle air conditioning system can be referenced. Figure 2 set up, Figure 2 A schematic diagram of components of a vehicle air conditioning system provided in an embodiment of this application is shown.

[0050] The vehicle air conditioning system includes a throttle valve 201, an evaporator 202, a controller 203, a condenser 204, and a compressor 205. These components are connected by refrigerant lines.

[0051] The expansion valve 201 can be located in the refrigerant cycle, and its main function is to regulate the flow and pressure of the refrigerant. When the high-temperature and high-pressure refrigerant flows out of the condenser 204, it is depressurized through the expansion valve 201, causing the refrigerant to change from a liquid state to a gas-liquid mixture, thereby lowering the temperature. This process creates conditions for the refrigerant in the evaporator 202 to absorb heat.

[0052] The condenser 204 is an important component of the vehicle's air conditioning system. It can be located at the front of the vehicle and is used to cool and liquefy the high-temperature, high-pressure refrigerant gas from the compressor 205. The condenser 204 completes the cooling and liquefaction process of the refrigerant by exchanging heat with the outside air, dissipating the heat in the refrigerant into the atmosphere.

[0053] Among them, the actual temperature of the evaporator 202 can be collected and sent to the controller 203.

[0054] Meanwhile, the actual refrigerant pressure collected in the refrigerant line between the evaporator 202 and the compressor 205 represents the low-side pressure of the vehicle's air conditioning system. This pressure is the refrigerant pressure at the suction end of the evaporator 202 and the compressor 205 during operation. The actual refrigerant pressure is collected in the refrigerant line between the evaporator 202 and the compressor 205 and sent to the controller 203.

[0055] The controller 203 determines the target compressor speed based on the actual temperature of the evaporator and the actual pressure of the refrigerant, and uses the target compressor speed to control the speed of the compressor 205.

[0056] The vehicle compressor control method provided in this application first obtains the target evaporator temperature in response to a user's temperature adjustment command, enabling adjustments based on the user's actual needs and improving user experience and comfort. Second, it determines the evaporator reference speed based on the target and actual evaporator temperatures. By monitoring the actual evaporator temperature in real time and comparing it with the target temperature, the compressor reference speed can be accurately calculated. Furthermore, it acquires the blower voltage and collects the evaporator inlet air temperature, introducing multiple parameters beyond just the evaporator temperature, thus improving the robustness of compressor speed control. Then, in a pre-calibrated refrigerant pressure gauge, it finds the target refrigerant pressure value based on the blower voltage and evaporator inlet air temperature. It uses a refrigerant pressure sensor to collect the actual refrigerant pressure value and determines the refrigerant pressure reference speed based on the target and actual refrigerant pressure values. Even if the evaporator temperature sensor is not correctly installed or malfunctions, or if there is a signal delay, the target refrigerant pressure value can still be determined based on the blower voltage and evaporator inlet air temperature, thereby determining an accurate refrigerant pressure reference speed. Finally, the target compressor speed is selected from the evaporator reference speed and the refrigerant pressure reference speed, and the compressor is controlled using the target compressor speed. The target compressor speed can be selected from two reference speeds, avoiding the problem that the compressor speed obtained by a single method may be inaccurate. This can obtain a more accurate compressor speed, improve the compressor control precision, and thus ensure the stability and reliability of the vehicle air conditioning system.

[0057] In one alternative embodiment of this application, the vehicle further includes an evaporator temperature sensor. Step 102 also includes the following steps: S11, The actual temperature of the evaporator is collected using the evaporator temperature sensor; S12, determine the evaporator temperature difference based on the target evaporator temperature and the actual evaporator temperature; S13, obtain the preset initial compressor speed, and determine the evaporator reference speed based on the initial compressor speed and the temperature difference of the evaporator.

[0058] In this embodiment, an evaporator temperature sensor can be used to collect the actual evaporator temperature, and the evaporator temperature difference can be determined based on the target evaporator temperature and the actual evaporator temperature. Then, a preset initial compressor speed is obtained, and an evaporator reference speed is determined based on the initial compressor speed and the evaporator temperature difference. The initial compressor speed can refer to the estimated compressor speed, representing the default speed in the initial or steady-state state of the system, and can be set according to actual conditions.

[0059] In practical implementation, the reference rotational speed of the evaporator can be calculated using the following formula:

[0060] in, Indicates the reference rotational speed of the evaporator. Indicates the initial speed of the compressor. Let dt represent the temperature difference in the evaporator, t represent time, and dt represent the infinitesimal and non-zero change in time. Indicates the temperature difference of the evaporator Accumulated amount over time, The proportional gain coefficient representing the temperature deviation. The integral gain coefficient represents the temperature deviation. and The specific value can be set according to the actual situation.

[0061] This application uses an evaporator temperature sensor to collect the actual evaporator temperature in real time and, combined with the difference between the target and actual evaporator temperatures, dynamically determines the evaporator reference rotation speed, thereby achieving precise control of the evaporator temperature. This not only improves the system's response speed and stability but also effectively reduces temperature fluctuations, enhancing the comfort and energy efficiency of the vehicle's air conditioning system. By introducing proportional and integral gain coefficients, intelligent adjustments can be made based on the magnitude and accumulation of temperature deviations, further optimizing the control effect.

[0062] In one optional embodiment of this application, step 105 further includes the following steps: S21, The actual pressure value of the refrigerant is collected using the refrigerant pressure sensor; S22, determine the refrigerant pressure difference based on the target refrigerant pressure value and the actual refrigerant pressure value; S23, obtain the preset initial compressor speed, and determine the refrigerant pressure reference speed based on the initial compressor speed and the refrigerant pressure difference.

[0063] In this embodiment, a refrigerant pressure sensor can be used to collect the actual refrigerant pressure value, and the refrigerant pressure difference can be determined based on the target refrigerant pressure value and the actual refrigerant pressure value. Then, a preset initial compressor speed is obtained, and a refrigerant pressure reference speed is determined based on the initial compressor speed and the refrigerant pressure difference. The initial compressor speed can refer to the estimated compressor speed, representing the default speed in the initial or steady-state state of the system, and can be set according to actual conditions.

[0064] In this embodiment, when the actual refrigerant pressure is less than the target refrigerant pressure, the refrigerant pressure reference speed gradually decreases. Reducing the refrigerant pressure reference speed decreases the refrigerant flow rate, preventing excessively low pressure. When the actual refrigerant pressure is greater than the target refrigerant pressure, the refrigerant pressure reference speed gradually increases. Increasing the refrigerant pressure reference speed increases the refrigerant flow rate, preventing excessively high pressure. When the actual refrigerant pressure equals the target refrigerant pressure, the refrigerant pressure reference speed remains relatively stable.

[0065] In practical implementation, the refrigerant pressure reference speed can be calculated using the following formula:

[0066] in, Indicates the refrigerant pressure reference speed. Indicates the initial speed of the compressor. dt represents the refrigerant pressure difference, t represents time, and dt represents an infinitesimal and non-zero change in time. Indicates the refrigerant pressure difference Accumulated amount over time, The proportional gain coefficient represents the pressure deviation. The integral gain coefficient represents the pressure deviation. and The specific value can be set according to the actual situation.

[0067] This application uses a refrigerant pressure sensor to collect the actual refrigerant pressure value in real time, and dynamically determines the refrigerant pressure reference speed by combining the difference between the target refrigerant pressure value and the actual pressure value. This not only improves the system's response speed and stability, but also effectively reduces pressure fluctuations, enhancing the energy efficiency and reliability of the vehicle's air conditioning system. By introducing proportional gain and integral gain coefficients, intelligent adjustments can be made based on the magnitude and accumulation of pressure deviations, further optimizing the control effect.

[0068] In one optional embodiment of this application, step 106 further includes the following steps: S31, if the evaporator reference speed is greater than the refrigerant pressure reference speed, then the refrigerant pressure reference speed is used as the target compressor speed, and the compressor is controlled using the target compressor speed; S32, if the evaporator reference speed is less than the refrigerant pressure reference speed, then the evaporator reference speed is used as the target compressor speed, and the compressor is controlled using the target compressor speed; S33, if the evaporator reference speed is equal to the refrigerant pressure reference speed, then the evaporator reference speed or the refrigerant pressure reference speed is taken as the target compressor speed, and the compressor is controlled by the target compressor speed.

[0069] In this embodiment of the application, if the evaporator reference speed is greater than the refrigerant pressure reference speed, the refrigerant pressure reference speed can be used as the target compressor speed, and the compressor can be controlled using the target compressor speed.

[0070] If the evaporator reference speed is less than the refrigerant pressure reference speed, the evaporator reference speed can be used as the target compressor speed, and the compressor can be controlled using the target compressor speed. If the evaporator reference speed is equal to the refrigerant pressure reference speed, then the evaporator reference speed or the refrigerant pressure reference speed can be used as the target compressor speed, and the compressor can be controlled using the target compressor speed.

[0071] In practice, the smaller of the evaporator reference speed and the refrigerant pressure reference speed can be selected as the target compressor speed, and the compressor can be controlled using the target compressor speed. This avoids the compressor from continuously operating at a high speed, thereby preventing evaporator frosting.

[0072] This application compares the evaporator reference speed and the refrigerant pressure reference speed, selecting the smaller one as the target compressor speed, and controls the compressor operation accordingly. This control strategy effectively balances the demands of evaporator temperature and refrigerant pressure, preventing the compressor from continuously operating at high speeds, thereby reducing the risk of evaporator frosting and extending equipment lifespan. Simultaneously, this method optimizes compressor efficiency, reduces energy consumption, and improves the overall energy efficiency of the system. By dynamically adjusting the compressor speed, it can respond flexibly to actual operating conditions, ensuring the stability and comfort of the air conditioning system under different environments, demonstrating high practicality and economy.

[0073] In one optional embodiment of this application, the refrigerant pressure gauge is calibrated in the following manner: S41, obtain a number of preset evaporator inlet air temperatures and a number of preset evaporator inlet air volumes; S42, In the preset vehicle simulation model, simulation is performed based on any of the evaporator inlet air temperature and any of the evaporator inlet air volume to obtain the refrigerant target pressure value; S43, construct an initial refrigerant pressure gauge based on the evaporator inlet air temperature, the evaporator inlet air volume and the refrigerant target pressure value; S44, In an actual vehicle, the blower voltage corresponding to the evaporator intake air volume is obtained by testing according to any of the evaporator intake air volumes. S45, in the initial refrigerant pressure gauge, for any evaporator inlet air volume, the blower voltage corresponding to the evaporator inlet air volume is used to replace the evaporator inlet air volume, so as to obtain the refrigerant pressure gauge composed of the evaporator inlet air temperature, the blower voltage and the refrigerant target pressure value.

[0074] In this embodiment of the application, several preset evaporator inlet air temperatures and several preset evaporator inlet air volumes can be obtained. Then, in a preset vehicle simulation model, simulation can be performed based on any evaporator inlet air temperature and any evaporator inlet air volume to obtain the target refrigerant pressure value.

[0075] The vehicle simulation model can be a computer-based virtual model used to simulate the operating state of a vehicle and its subsystems, such as an air conditioning system, under different working conditions. By inputting various parameters, the simulation model can calculate the corresponding output results. It can be applied to vehicle design, performance optimization, and control system development. In this embodiment, the target refrigerant pressure value can be determined in the vehicle simulation model.

[0076] In this embodiment, an initial refrigerant pressure gauge can be constructed based on the evaporator inlet air temperature, evaporator inlet air volume, and target refrigerant pressure. The initial refrigerant pressure gauge is a table used to represent the correspondence between the evaporator inlet air temperature, evaporator inlet air volume, and target refrigerant pressure.

[0077] It is understandable that any target refrigerant pressure value in the initial refrigerant pressure gauge is obtained by simulating the evaporator inlet air temperature and evaporator inlet air volume corresponding to that target refrigerant pressure value in the preset vehicle simulation model.

[0078] In a practical implementation, the initial refrigerant pressure gauge can be in the form shown in Table 2 below: Table 2 Initial Refrigerant Pressure Gauge

[0079] In this embodiment of the application, in an actual vehicle, the blower voltage corresponding to any evaporator intake air volume can be obtained by testing.

[0080] In practical implementation, the blower voltage corresponding to the evaporator inlet air volume can be stored in the inlet voltage calibration table. The inlet voltage calibration table can be set with reference to Table 3 below: Table 3 Inlet Voltage Calibration Table

[0081] In this embodiment of the application, in the initial refrigerant pressure gauge, for any evaporator inlet air volume, the blower voltage corresponding to the evaporator inlet air volume can be used to replace the evaporator inlet air volume, so as to obtain a refrigerant pressure gauge composed of evaporator inlet air temperature, blower voltage and refrigerant target pressure value.

[0082] The refrigerant pressure gauge is a table used to show the relationship between the evaporator inlet air temperature, blower voltage, and target refrigerant pressure. The refrigerant pressure gauge can be set up according to the format of Table 1 above.

[0083] In this embodiment, after obtaining the refrigerant pressure gauge, it can be verified in an actual vehicle. Specifically, the actual vehicle can be controlled according to the evaporator intake airflow and blower voltage in Table 1 (refrigerant pressure gauge). When the actual evaporator temperature matches the evaporator calibration temperature, a refrigerant pressure sensor is used to collect the refrigerant verification pressure value. The verification pressure value is then checked against the target refrigerant pressure value. If they match, the refrigerant pressure gauge is correctly calibrated. If they do not match, the verification pressure value replaces the target refrigerant pressure value in the refrigerant pressure gauge.

[0084] This application constructs an accurate refrigerant pressure gauge by combining vehicle simulation modeling with actual vehicle calibration. First, an initial refrigerant pressure gauge is obtained using the vehicle simulation model based on parameters such as evaporator inlet air temperature and airflow. Then, the blower voltage is obtained by testing the airflow in an actual vehicle, and this blower voltage is used to replace the airflow in the initial refrigerant pressure gauge to obtain the final refrigerant pressure gauge. This dual calibration method, from vehicle simulation model to actual vehicle calibration, not only improves the accuracy of the refrigerant pressure gauge but also provides an effective and reliable foundation for the control of the vehicle's air conditioning system.

[0085] In one optional embodiment of this application, step S42 further includes the following sub-steps: S51, obtain the preset evaporator calibration temperature; S52, In the preset vehicle simulation model, simulation is performed based on any of the evaporator inlet air temperature and any of the evaporator inlet air volume, and the evaporator reference temperature in the vehicle simulation model is collected. S53, when the evaporator reference temperature is consistent with the evaporator calibration temperature, the refrigerant pressure value in the vehicle simulation model is used as the refrigerant target pressure value.

[0086] In this embodiment, a preset evaporator calibration temperature can be obtained. This evaporator calibration temperature can be a target evaporator temperature set during the calibration process, and can be set according to actual needs.

[0087] In this embodiment of the application, in the preset vehicle simulation model, simulation can be performed based on any evaporator inlet air temperature and any evaporator inlet air volume, and the evaporator reference temperature in the vehicle simulation model can be collected. When the evaporator reference temperature is consistent with the evaporator calibration temperature, the refrigerant pressure value in the vehicle simulation model can be used as the refrigerant target pressure value.

[0088] In practical implementation, taking an evaporator calibration temperature of 3℃ as an example, different evaporator inlet air volumes and evaporator inlet air temperatures can be input into the vehicle simulation model according to Table 2. For example, the evaporator inlet air volume can be input as 100m³ / h. 3 / h, the evaporator inlet air temperature is 10℃. When the actual evaporator temperature is 3℃, the refrigerant pressure value a0 in the vehicle simulation model is obtained and filled into Table 2 as the refrigerant target pressure value. It can be understood that the correspondence in Table 2 is an example, and the specific correspondence between evaporator inlet air temperature, evaporator inlet air volume and refrigerant target pressure value can be calibrated according to the actual situation.

[0089] This application uses a pre-set vehicle simulation model, combined with evaporator inlet air temperature and airflow, to accurately obtain the evaporator reference temperature. When this temperature matches the calibration temperature, the refrigerant pressure value in the simulation model is used as the target pressure value. Through simulation, parameters can be flexibly adjusted, and the target refrigerant pressure value can be quickly obtained, improving the accuracy of refrigeration system calibration.

[0090] In an optional embodiment of this application, step S44 further includes the following sub-steps: S61, In an actual vehicle, the air intake air volume of any of the evaporators is tested, and the measured air volume of the evaporator in the actual vehicle is collected. S62, if the measured air volume of the evaporator is consistent with the air volume of the evaporator intake, the blower voltage in the actual vehicle is taken as the blower voltage corresponding to the air volume of the evaporator intake.

[0091] In this embodiment of the application, in an actual vehicle, the air intake air volume of any evaporator is tested, and the measured air volume of the evaporator in the actual vehicle is collected. When the measured air volume of the evaporator is consistent with the air intake air volume of the evaporator, the blower voltage in the actual vehicle can be used as the blower voltage corresponding to the air intake air volume of the evaporator.

[0092] Among them, testing in actual vehicles can be conducted in test stations, test environments, or real road conditions using actual vehicles.

[0093] In practical implementation, the blower voltage corresponding to different evaporator intake air volumes can be measured using an actual vehicle on an air volume testing bench, thus establishing a mapping relationship between the blower voltage and the evaporator intake air volume. Taking Table 3 as an example, an evaporator intake air volume of 100m³ / h can be measured using an actual vehicle at a testing station, such as an air volume testing bench. 3 At a rate of / h, the corresponding blower voltage is 3V. It is understood that the correspondence in Table 3 is an example; the specific correspondence between evaporator inlet air temperature and blower voltage can be determined based on actual conditions.

[0094] This application embodiment ensures consistency between blower voltage and evaporator airflow by testing the correspondence between evaporator intake airflow and blower voltage in actual vehicles. Through actual testing, This avoids discrepancies between the vehicle simulation model and the actual vehicle, further ensuring the accuracy and applicability of the refrigerant pressure gauge.

[0095] In practical implementation, the compressor control process can be referenced. Figure 3 conduct, Figure 3 A flowchart illustrating the steps of compressor control according to an embodiment of this application is shown.

[0096] The evaporator temperature difference can be determined based on the target evaporator temperature and the actual evaporator temperature, and the evaporator reference speed can be further determined. The specific determination method can be referred to the embodiments of this application.

[0097] The refrigerant pressure difference can be determined based on the target refrigerant pressure value and the actual refrigerant pressure value, and the refrigerant pressure reference speed can be further determined. The specific determination method can be referred to the embodiments of this application.

[0098] Select the target compressor speed from the evaporator reference speed and the refrigerant pressure reference speed, and use the target compressor speed to control the compressor.

[0099] In practical implementation, the evaporator temperature control effect can be referenced. Figure 4 , Figure 4 A comparison diagram of the control effect of evaporator temperature provided in an embodiment of this application is shown.

[0100] in, Figure 4 The curves in the figure represent the evaporator temperature curves of related technologies and the evaporator temperature curves of this application, respectively. Figure 4 The horizontal axis represents time, and the vertical axis represents evaporator temperature.

[0101] Taking the target temperature of the evaporator as 3℃ as an example, two cooling curves of the evaporator from the initial temperature of 30℃ to 3℃ were obtained by using relevant technologies and the method of this application.

[0102] By superimposing the two curves above and comparing their evaporator temperature control effects, the evaporator temperature curve of this application shows that the evaporator temperature control is more stable.

[0103] In practical implementation, the effect of compressor speed control can be referenced. Figure 5 , Figure 5 A comparison diagram of the control effect of compressor speed provided in an embodiment of this application is shown.

[0104] in, Figure 5 The curves in the figure represent the compressor speed curves of related technologies and the compressor speed curves of this application, respectively. Figure 5 The horizontal axis represents time, and the vertical axis represents compressor speed.

[0105] Taking the target evaporator temperature set at 3℃ as an example, two compressor speed curves were obtained by testing the compressor speed from high speed to 0 speed using relevant technologies and the method of this application.

[0106] By superimposing the two curves above and comparing the control effect of compressor speed, the compressor speed curve of this application shows that the high-speed operation time of the compressor is significantly shortened.

[0107] In the actual implementation, frosting performance was verified in a real vehicle. The evaporator temperature sensor was removed from the vehicle's air conditioning system to simulate a faulty or improperly installed sensor. The frosting performance was then verified using the vehicle compressor control method described in this application. The air conditioning fan speed was set to level 1, the temperature to the lowest setting, and external air circulation was enabled. The vehicle speed was set to random (including urban and highway conditions), and the presence of frost on the evaporator was observed. After two hours of actual road testing, no frost was observed.

[0108] Reference Figure 6 The diagram illustrates a structural schematic of a task allocation device according to an embodiment of this application. The vehicle further includes a blower, an evaporator, and a compressor. The evaporator and the compressor are connected via a refrigerant pipeline. A refrigerant pressure sensor is installed in the refrigerant pipeline. The device includes: The target temperature acquisition module 601 is used to acquire the target evaporator temperature corresponding to the temperature adjustment command issued by the user in response to the temperature adjustment command. The first rotation speed determination module 602 is used to collect the actual temperature of the evaporator and determine the reference rotation speed of the evaporator based on the target temperature and the actual temperature of the evaporator. The voltage and temperature acquisition module 603 is used to acquire the blower voltage of the blower and the evaporator inlet air temperature of the evaporator; The target pressure determination module 604 is used to find the target refrigerant pressure value in a pre-calibrated refrigerant pressure table based on the blower voltage and the evaporator inlet air temperature. The second speed determination module 605 is used to collect the actual pressure value of the refrigerant using the refrigerant pressure sensor, and determine the refrigerant pressure reference speed based on the target pressure value of the refrigerant and the actual pressure value of the refrigerant. The target speed determination module 606 is used to select a target compressor speed from the evaporator reference speed and the refrigerant pressure reference speed, and to control the compressor using the target compressor speed.

[0109] In one optional embodiment of this application, the vehicle further includes an evaporator temperature sensor, and the first rotational speed determination module 602 includes: The temperature acquisition submodule is used to acquire the actual temperature of the evaporator using the evaporator temperature sensor. The temperature difference determination submodule is used to determine the evaporator temperature difference value based on the evaporator target temperature and the evaporator actual temperature. The first speed determination submodule is used to obtain the preset initial compressor speed and determine the evaporator reference speed based on the initial compressor speed and the temperature difference of the evaporator.

[0110] In one optional embodiment of this application, the second rotational speed determining module 605 includes: The pressure acquisition submodule is used to acquire the actual pressure value of the refrigerant using the refrigerant pressure sensor. The pressure difference determination submodule is used to determine the refrigerant pressure difference based on the target refrigerant pressure value and the actual refrigerant pressure value. The second speed determination submodule is used to obtain the preset initial compressor speed and determine the refrigerant pressure reference speed based on the initial compressor speed and the refrigerant pressure difference.

[0111] In one optional embodiment of this application, the target rotational speed determination module 606 includes: The first target speed determination submodule is used to determine the compressor speed by taking the refrigerant pressure reference speed as the target compressor speed if the evaporator reference speed is greater than the refrigerant pressure reference speed, and to control the compressor using the target compressor speed. The second target speed determination submodule is used to determine the target compressor speed if the evaporator reference speed is less than the refrigerant pressure reference speed, and to control the compressor using the target compressor speed. The third target speed determination submodule is used to determine the target compressor speed if the evaporator reference speed is equal to the refrigerant pressure reference speed, and to control the compressor using the target compressor speed.

[0112] In one optional embodiment of this application, the refrigerant pressure gauge is calibrated in the following manner: The calibration parameter acquisition submodule is used to acquire several preset evaporator inlet air temperatures and several preset evaporator inlet air volumes. The simulation model calibration submodule is used to perform simulation in a preset vehicle simulation model based on any of the evaporator inlet air temperature and any of the evaporator inlet air volume, and obtain the refrigerant target pressure value. The initial pressure gauge calibration submodule is used to construct an initial refrigerant pressure gauge based on the evaporator inlet air temperature, the evaporator inlet air volume, and the refrigerant target pressure value. The actual vehicle calibration submodule is used to test the evaporator intake air volume in an actual vehicle to obtain the blower voltage corresponding to the evaporator intake air volume. The target pressure gauge calibration submodule is used to replace the evaporator inlet air volume with the blower voltage corresponding to the evaporator inlet air volume for any given evaporator inlet air volume in the initial refrigerant pressure gauge, thereby obtaining the refrigerant pressure gauge composed of the evaporator inlet air temperature, the blower voltage, and the refrigerant target pressure value.

[0113] In one optional embodiment of this application, the simulation model calibration submodule includes: The calibration temperature acquisition unit is used to acquire the preset evaporator calibration temperature; The simulation model calibration unit is used to perform simulation in a preset vehicle simulation model based on any of the evaporator inlet air temperatures and any of the evaporator inlet air volumes, and to collect the evaporator reference temperature in the vehicle simulation model. The target pressure value determination unit is used to take the refrigerant pressure value in the vehicle simulation model as the refrigerant target pressure value when the evaporator reference temperature is consistent with the evaporator calibration temperature.

[0114] In one optional embodiment of this application, the actual vehicle calibration submodule includes: The actual vehicle calibration unit is used to test the air intake air volume of any of the evaporators in an actual vehicle and to collect the measured air volume of the evaporator in the actual vehicle. The blower voltage determination unit is used to determine the blower voltage in the actual vehicle as the blower voltage corresponding to the evaporator inlet air volume when the measured air volume of the evaporator is consistent with the air volume of the evaporator inlet air volume.

[0115] As the apparatus embodiment is basically similar to the method embodiment, it is described in a relatively simple manner. For relevant details, please refer to the description of the method embodiment.

[0116] One embodiment of this application also provides a vehicle that may include a processor, a memory, and a computer program stored in the memory and capable of running on the processor, wherein the computer program, when executed by the processor, implements the method described above.

[0117] An embodiment of this application also provides a computer-readable storage medium on which a computer program is stored, and when the computer program is executed by a processor, it implements the method described above.

[0118] It should be noted that the user information (including but not limited to user device information, user personal information, etc.) and data (including but not limited to data used for analysis, data stored, data displayed, etc.) involved in this application are all information and data authorized by the user or fully authorized by all parties. Furthermore, the collection, use and processing of the relevant data must comply with the relevant laws, regulations and standards of the relevant countries and regions, and corresponding operation entry points are provided for users to choose to authorize or refuse.

[0119] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0120] Those skilled in the art will understand that embodiments of this application can be provided as methods, apparatus, or computer program products. Therefore, embodiments of this application can take the form of entirely hardware embodiments, entirely software embodiments, or embodiments combining software and hardware aspects. Furthermore, embodiments of this application can take the form of computer program products implemented 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.

[0121] This application describes embodiments with reference to flowchart illustrations and / or block diagrams of methods, terminal devices (systems), and computer program products according to embodiments of this application. It should 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 terminal device to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing terminal device, generate instructions for implementing the flowchart illustrations. Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0122] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing terminal device to operate 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.

[0123] These computer program instructions can also be loaded onto a computer or other programmable data processing terminal equipment, causing a series of operational steps to be performed on the computer or other programmable terminal equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable terminal 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.

[0124] Although preferred embodiments of the present application have been described, those skilled in the art, upon learning the basic inventive concept, can make other modifications and updates to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments as well as all modifications and updates falling within the scope of the embodiments of the present application.

[0125] Finally, it should be noted that in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or terminal device 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 terminal device. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or terminal device that includes the aforementioned element.

[0126] The above provides a detailed description of the control method, device, vehicle, and medium for a vehicle compressor. Specific examples have been used to illustrate the principles and implementation methods of this application. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of this application. At the same time, those skilled in the art will recognize that there will be changes in the specific implementation methods and application scope based on the ideas of this application. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A control method of a vehicle compressor, characterized by, The vehicle also includes a blower, an evaporator and a compressor, the evaporator and the compressor being connected by a refrigerant pipeline, a refrigerant pressure sensor being arranged in the refrigerant pipeline, and the method comprises: In response to a temperature adjustment instruction issued by a user, an evaporator target temperature corresponding to the temperature adjustment instruction is acquired; An evaporator actual temperature of the evaporator is collected, and an evaporator reference speed is determined according to the evaporator target temperature and the evaporator actual temperature; A blower voltage of the blower is acquired, and an evaporator inlet air temperature of the evaporator is collected; In a pre-calibrated refrigerant pressure table, a refrigerant target pressure value is found according to the blower voltage and the evaporator inlet air temperature; A refrigerant actual pressure value is collected by using the refrigerant pressure sensor, and a refrigerant pressure reference speed is determined according to the refrigerant target pressure value and the refrigerant actual pressure value; A target compressor speed is selected from the evaporator reference speed and the refrigerant pressure reference speed, and the compressor is controlled by using the target compressor speed.

2. The method of claim 1, wherein, The vehicle also includes an evaporator temperature sensor, and the collection of the evaporator actual temperature of the evaporator and the determination of the evaporator reference speed according to the evaporator target temperature and the evaporator actual temperature comprise: The evaporator actual temperature of the evaporator is collected by using the evaporator temperature sensor; An evaporator temperature difference value is determined according to the evaporator target temperature and the evaporator actual temperature; A preset compressor initial speed is acquired, and the evaporator reference speed is determined according to the compressor initial speed and the evaporator temperature difference value.

3. The method of claim 1, wherein, The collection of the refrigerant actual pressure value by using the refrigerant pressure sensor and the determination of the refrigerant pressure reference speed according to the refrigerant target pressure value and the refrigerant actual pressure value comprise: The refrigerant actual pressure value is collected by using the refrigerant pressure sensor; A refrigerant pressure difference value is determined according to the refrigerant target pressure value and the refrigerant actual pressure value; A preset compressor initial speed is acquired, and the refrigerant pressure reference speed is determined according to the compressor initial speed and the refrigerant pressure difference value.

4. The method of claim 1, wherein, The selection of the target compressor speed from the evaporator reference speed and the refrigerant pressure reference speed and the control of the compressor by using the target compressor speed comprise: If the evaporator reference speed is greater than the refrigerant pressure reference speed, the refrigerant pressure reference speed is taken as the target compressor speed, and the compressor is controlled by using the target compressor speed; If the evaporator reference speed is less than the refrigerant pressure reference speed, the evaporator reference speed is taken as the target compressor speed, and the compressor is controlled by using the target compressor speed; If the evaporator reference speed is equal to the refrigerant pressure reference speed, the evaporator reference speed or the refrigerant pressure reference speed is taken as the target compressor speed, and the compressor is controlled by using the target compressor speed.

5. The method of claim 1, wherein, The refrigerant pressure table is calibrated in the following manner: A plurality of preset evaporator inlet air temperatures and a plurality of preset evaporator inlet air quantities are acquired; In a preset vehicle simulation model, simulation is performed according to any of the evaporator inlet air temperatures and any of the evaporator inlet air volumes, to obtain refrigerant target pressure values; An initial refrigerant pressure table is constructed according to the evaporator inlet air temperatures, the evaporator inlet air volumes and the refrigerant target pressure values; In an actual vehicle, testing is performed according to any of the evaporator inlet air volumes, to obtain blower voltages corresponding to the evaporator inlet air volumes; In the initial refrigerant pressure table, for any of the evaporator inlet air volumes, the blower voltage corresponding to the evaporator inlet air volume is used to replace the evaporator inlet air volume, to obtain a refrigerant pressure table composed of the evaporator inlet air temperatures, the blower voltages and the refrigerant target pressure values.

6. The method of claim 5, wherein, The simulation in the preset vehicle simulation model according to any of the evaporator inlet air temperatures and any of the evaporator inlet air volumes to obtain refrigerant target pressure values comprises: A preset evaporator calibration temperature is obtained; In a preset vehicle simulation model, simulation is performed according to any of the evaporator inlet air temperatures and any of the evaporator inlet air volumes, and an evaporator reference temperature in the vehicle simulation model is collected; In the case where the evaporator reference temperature is consistent with the evaporator calibration temperature, a refrigerant pressure value in the vehicle simulation model is taken as a refrigerant target pressure value.

7. The method of claim 5, wherein, The testing in an actual vehicle according to any of the evaporator inlet air volumes to obtain blower voltages corresponding to the evaporator inlet air volumes comprises: In an actual vehicle, testing is performed according to any of the evaporator inlet air volumes, and an evaporator measured air volume in the actual vehicle is collected; In the case where the evaporator measured air volume is consistent with the evaporator inlet air volume, a blower voltage in the actual vehicle is taken as a blower voltage corresponding to the evaporator inlet air volume.

8. A control device of a vehicle compressor characterized by comprising: The vehicle further comprises a blower, an evaporator and a compressor, the evaporator and the compressor being connected through a refrigerant pipeline, a refrigerant pressure sensor being arranged in the refrigerant pipeline, and the device comprises: A target temperature acquisition module is configured to acquire an evaporator target temperature corresponding to a temperature adjustment instruction issued by a user in response to the temperature adjustment instruction; A first rotating speed determination module is configured to collect an evaporator actual temperature of the evaporator, and determine an evaporator reference rotating speed according to the evaporator target temperature and the evaporator actual temperature; A voltage and temperature collection module is configured to acquire a blower voltage of the blower, and collect an evaporator inlet air temperature of the evaporator; A target pressure determination module is configured to find a refrigerant target pressure value in a pre-calibrated refrigerant pressure table according to the blower voltage and the evaporator inlet air temperature; A second rotating speed determination module is configured to collect a refrigerant actual pressure value by using the refrigerant pressure sensor, and determine a refrigerant pressure reference rotating speed according to the refrigerant target pressure value and the refrigerant actual pressure value; A target rotating speed determination module is configured to select a target compressor rotating speed from the evaporator reference rotating speed and the refrigerant pressure reference rotating speed, and control the compressor by using the target compressor rotating speed.

9. A vehicle characterized by comprising: A computer program product comprising a computer readable storage medium having stored thereon computer program means, the computer program means comprising computer readable program code configured to, when executed on a processor, cause the processor to carry out the method according to any of claims 1-7.

10. A computer-readable storage medium, characterized in that, A computer program product comprising a computer readable storage medium having stored thereon computer program means, the computer program means comprising computer readable program code configured to, when executed on a processor, cause the processor to carry out the method according to any of claims 1-7.

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