Thermal management system control method, apparatus, and device

Abstract

This application provides a thermal management system control method. A first influencing factor is determined based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature. The opening of the heating throttling valve is then adjusted based on the first influencing factor and the current cycle's heating throttling valve opening increment. This method can take into account the impact of compressor speed changes on the high-pressure side pressure when controlling the actual outlet air temperature, resulting in more precise control of the heating throttling valve. This application also provides a thermal management system control device and equipment.

Description

Technical Field

[0001] This application relates to the field of thermal management control, and more particularly to a control method, apparatus and equipment for a thermal management system for vehicles. Background Technology

[0002] In related technologies, in a series dehumidification and heating mode, the thermal management system connects the compressor, condenser, heating expansion valve, outdoor heat exchanger, evaporator expansion valve, and evaporator in series. The heating expansion valve is connected to the condenser outlet, and the evaporator expansion valve is connected to the evaporator inlet. The thermal management system controls the outlet air temperature through the compressor, the optimal pressure through the heating expansion valve, and the evaporator surface temperature through the evaporator expansion valve. Changes in compressor speed affect the high-pressure and low-pressure sides of the thermal management system. When the heating expansion valve controls the high-pressure side, it affects the outlet air temperature and evaporator temperature. Related technologies employ extensive experimental calibration to determine the relationship between the heating expansion valve and the compressor's adjustment rate, thus enabling the regulation of the heating expansion valve. However, under limited experimental conditions, the experimental calibration method cannot adequately cover multiple operating conditions, resulting in poor accuracy in regulating the heating expansion valve. Summary of the Invention

[0003] This application aims to provide a control method for a thermal management system, which is designed to more accurately regulate the heating throttling valve.

[0004] To achieve the above objectives, this application provides a thermal management system control method, which determines a first influencing factor based on the actual exhaust pressure, target exhaust pressure, target air outlet temperature, and actual air outlet temperature, and adjusts the opening of the heating throttling valve based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle.

[0005] The thermal management system control method provided in this application determines the first influencing factor by using the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature. Based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle, the opening degree of the heating throttling valve is regulated. This method can take into account the influence of compressor speed changes on high-pressure side pressure when controlling the actual outlet air temperature, and the regulation of the heating throttling valve is more precise.

[0006] To achieve the above objectives, this application also provides a thermal management system control device, including a determination module and a control module. The determination module is used to determine a first influencing factor based on the actual exhaust pressure, the target exhaust pressure, the target outlet air temperature, and the actual outlet air temperature. The control module is used to regulate the opening of the heating throttling valve based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle.

[0007] The thermal management system control device provided in this application determines the first influencing factor by the module based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature. The control module then adjusts the opening of the heating throttling valve based on the first influencing factor and the current cycle heating throttling valve opening increment value. This approach can take into account the impact of compressor speed changes on high-pressure side pressure when controlling the actual outlet air temperature, resulting in more precise control of the heating throttling valve.

[0008] To achieve the above objectives, this application also provides a thermal management system control device, including a processor, a memory, and a thermal management system control program stored in the memory and executable by the processor, wherein when the thermal management system control program is executed by the processor, it implements the steps of the above-described thermal management system control method.

[0009] The thermal management system control device provided in this application, when the thermal management system control program is executed by the processor, determines a first influencing factor based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature and actual outlet air temperature, and adjusts the opening of the heating throttling valve based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle, which can take into account the influence of compressor speed change on high-pressure side pressure when controlling actual outlet air temperature, and make the control of the heating throttling valve more precise. Attached Figure Description

[0010] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some of the accompanying drawings of the embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0011] Figure 1 This is a flowchart illustrating an embodiment of a thermal management system control method provided in this application;

[0012] Figure 2 This is a schematic flowchart of another embodiment of the thermal management system control method provided in this application;

[0013] Figure 3 yes Figure 1 and Figure 2 A flowchart illustrating the determination of the first influencing factor in a thermal management system control method provided in the paper;

[0014] Figure 4 This is a flowchart illustrating another embodiment of the thermal management system control method provided in this application;

[0015] Figure 5 This is a flowchart illustrating another embodiment of the thermal management system control method provided in this application;

[0016] Figure 6 yes Figure 4 and Figure 5 A flowchart illustrating the determination of the second influencing factor in a thermal management system control method provided in this application;

[0017] Figure 7 This is a schematic block diagram of one embodiment of a thermal management system control device provided in this application;

[0018] Figure 8 This is a schematic block diagram of one embodiment of a thermal management system control device provided in this application. Detailed Implementation

[0019] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0020] Please see Figure 1 This application provides a control method for a thermal management system. A first influencing factor is determined based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature. The opening of the heating throttling valve is then adjusted based on this first influencing factor and the current cycle's heating throttling valve opening increment. This method determines the first influencing factor using the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature, and adjusts the heating throttling valve opening based on this first influencing factor and the current cycle's heating throttling valve opening increment. This approach can take into account the impact of compressor speed changes on the high-pressure side pressure when controlling the actual outlet air temperature, resulting in more precise control of the heating throttling valve.

[0021] In some embodiments, the step of regulating the opening degree of the heating throttling valve based on a first influencing factor and the current cycle heating throttling valve opening increment includes: the relationship between the first influencing factor and the heating throttling valve opening satisfies:

[0022] u H (n)=u H (n-1)+△u H (n)*α H

[0023] Among them, u H (n) represents the current cycle heating throttle valve opening output value, u H (n-1) represents the output value of the heating throttling valve opening in the previous cycle, Δu H (n) represents the increment of the opening of the heating throttling valve in the current cycle, α H It is the number one impact factor.

[0024] In a specific embodiment, the first influencing factor, also known as the high-pressure side influencing factor of the system, is used to regulate the opening degree of the high-pressure side heating throttle valve. Regulating the opening degree of the heating throttle valve based on the first influencing factor and the current cycle's heating throttle valve opening increment reduces the time and cost associated with extensive calibration and mitigates the problem of not being able to exhaustively account for multiple operating conditions.

[0025] Among them, the first influencing factor ≥ 0 indicates the influence on the adjustment rate of the heating throttling valve, Δu H (n) represents increments with positive and negative values. The first influence factor uses 1 as a balance point; the further it is from 1, the greater the influence. When the first influence factor is greater than 1, it correlates with the execution rate Δu. H Multiplying (n) will increase the adjustment rate of the heating throttling valve, indicating that the heating throttling valve needs to perform faster adjustments; when the first influence factor is less than 1, it is related to the execution rate Δu H (n) multiplication will suppress the adjustment rate of the heating throttle valve, and the adjustment of the heating throttle valve will become even slower.

[0026] In some embodiments, the step of determining the first influencing factor based on the actual exhaust pressure, the target exhaust pressure, the target outlet air temperature, and the actual outlet air temperature includes: determining the first influencing factor by selecting to perform operation one, operation two, or operation three based on the relationship between the actual exhaust pressure and the target exhaust pressure.

[0027] Operation 1 is that as ΔT increases, α H Decrease or remain unchanged;

[0028] Operation 2 is that as ΔT increases, α H Increase or remain unchanged;

[0029] Operation 3 is that as ΔT increases, α H Remain unchanged;

[0030] Where △T equals the target outlet air temperature minus the actual outlet air temperature.

[0031] In some embodiments, a first influencing factor is determined based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature. Since the actual outlet air temperature is related to the compressor speed, the influence of the compressor speed on the high-pressure side can be taken into account, thereby improving the control accuracy of the heating throttling valve.

[0032] Please see Figure 2 In some embodiments, before determining the first influencing factor, the steps of obtaining the actual exhaust pressure, the target exhaust pressure, the target outlet air temperature, and the actual outlet air temperature are further included.

[0033] Please see Figure 3In some embodiments, the step of determining the first influencing factor by selecting to perform operation one, operation two, or operation three based on the relationship between the actual exhaust pressure and the target exhaust pressure includes: when the actual exhaust pressure < the target exhaust pressure - ΔQ, operation one is selected. In this case, as ΔT increases, α H Decrease or remain unchanged, where ΔQ≥0; in some embodiments, when operation one is performed and ΔT≥0 is satisfied, 0≤α H ≤1; When operation one is executed and ΔT < 0, α H ≥1.

[0034] In some embodiments, denoted as △T1<△T2<0<△T3<△T4, the heating throttling valve is regulated in the following manner:

[0035] In some embodiments, when ΔT < ΔT1 < 0, and the actual outlet air temperature far exceeds the target outlet air temperature, the compressor needs to significantly reduce its speed. This significantly reduces the pressure on the high-pressure side. Since the actual exhaust pressure is low at this time, the opening of the heating throttling valve needs to be reduced to increase the actual exhaust pressure. Under the influence of the compressor speed, the heating throttling valve needs to compensate for this. For example: at this time, α H =max, as ΔT increases, α H It can exhibit a trend of remaining unchanged, where max > 1.

[0036] In some embodiments, when △T1≤△T≤△T2<0, as △T increases, α H The trend shows a gradual decrease. The closer the actual outlet air temperature is to the target outlet air temperature range, and the larger it is, the lower the compressor speed becomes, approaching the steady-state speed. At this point, the impact on the reduction of high pressure on the high-pressure side weakens, meaning the impact on the heating throttling valve on the high-pressure side weakens. Because the actual exhaust pressure is lower at this time, the opening of the heating throttling valve needs to be reduced to increase the actual exhaust pressure. Under the influence of the compressor speed, the heating throttling valve needs to compensate for this. At this point, the further the actual outlet air temperature is from the target outlet air temperature, the greater the impact of the compressor speed, α. H Gradually increase; conversely, the closer the actual outlet air temperature is to the target outlet air temperature range, the smaller the impact of compressor speed. H Gradually decrease until it approaches 1. For example, at this point, 1 ≤ α. H ≤max, where max>1, as ΔT increases, the actual outlet air temperature gets closer to the target outlet air temperature range, α HIt can show a decreasing trend. In other words, at this time, the actual outlet air temperature has exceeded the target outlet air temperature, and the compressor needs to reduce its speed to reach the target outlet air temperature. The decrease in speed also causes a decrease in the actual exhaust pressure. The heating throttling valve originally needs to reduce the valve opening to increase the high-pressure side pressure in order to reach the target exhaust pressure. At this time, it needs to reduce the valve opening even faster.

[0037] In some embodiments, when ΔT2 < ΔT < ΔT3, the closer the actual outlet air temperature is to the target outlet air temperature range, the more stable the compressor speed becomes. In this case, the impact on the high-pressure side is smaller, and the heating throttling valve on the high-pressure side can adjust normally according to the given adjustment speed. At this time, α H It tends to 1, and as ΔT increases, α H It can exhibit a trend that remains unchanged.

[0038] In some embodiments, 0 < ΔT3 ≤ ΔT ≤ ΔT4, the closer the actual outlet air temperature is to the target outlet air temperature range and the smaller it is, the closer the compressor speed increases to the steady-state speed. At this point, the impact on the high-pressure side gradually weakens, and the adjustment of the high-pressure side relies more on the heating expansion valve. Furthermore, increasing the compressor speed will cause an increase in the actual discharge pressure. Since the actual discharge pressure is low at this time, the opening of the heating expansion valve needs to be reduced to increase the actual discharge pressure. Under the influence of the compressor speed, the opening adjustment of the heating expansion valve itself needs to be slowed down to compensate for this. At this time, the farther the actual outlet air temperature is from the target outlet air temperature range, the greater the impact of the compressor speed, α H Gradually decrease; conversely, the closer the actual outlet air temperature is to the target outlet air temperature, the smaller the impact of compressor speed. H Gradually increase until it approaches 1, for example: at this point, 0 ≤ α H ≤1, as ΔT increases, α H It may show a decreasing trend.

[0039] In some embodiments, when ΔT > ΔT4 > 0, and the actual outlet air temperature is much lower than the target outlet air temperature range, the compressor speed needs to continue to increase, which has a significant impact on the increase of high pressure on the high-pressure side. Since the actual exhaust pressure is low at this time, the opening of the heating throttling valve needs to be reduced to increase the actual exhaust pressure. Under the influence of the compressor speed, to ensure the single controllability of the variable, the opening regulation of the heating throttling valve on the high-pressure side is weakened. For example: at this time, α... H α is equal to or close to 0, and as ΔT increases, α H It can exhibit a trend that remains unchanged.

[0040] Please see Figure 2In some embodiments, the step of determining the first influencing factor by selecting to perform operation one, operation two, or operation three based on the relationship between the actual exhaust pressure and the target exhaust pressure includes: when the actual exhaust pressure > the target exhaust pressure + ΔQ, operation two is selected. In this case, as ΔT increases, α H Increase or remain unchanged, where ΔQ≥0; in some specific embodiments, when operation two is performed and ΔT≥0 is satisfied, α H ≥1; When operation two is executed and ΔT < 0, 0 ≤ α H ≤1.

[0041] In some embodiments, denoted as △T1<△T2<0<△T3<△T4, the heating throttling valve is regulated in the following manner:

[0042] In some embodiments, when ΔT < ΔT1 < 0, and the actual outlet air temperature far exceeds the target outlet air temperature, the compressor needs to significantly reduce its speed. This significantly reduces the pressure on the high-pressure side. Because the actual exhaust pressure is too high at this time, the opening of the heating throttle valve needs to be increased to reduce the actual exhaust pressure. At this point, due to the influence of the compressor speed, the opening adjustment of the heating throttle valve itself needs to be slowed down to compensate for the impact of the reduced compressor speed. For example: at this time, α H =0.4, since the actual outlet air temperature is much higher than the target outlet air temperature, as ΔT increases, α H It can exhibit a trend that remains unchanged, staying at a relatively small value.

[0043] In some embodiments, when △T1≤△T≤△T2<0, as △T increases, α H The trend shows a gradual increase. At this point, the actual outlet air temperature exceeds the target outlet air temperature, requiring the compressor to reduce its speed, which reduces the impact on the high-pressure side. Because the actual exhaust pressure is higher at this time, the heating throttling valve itself needs to increase its opening to reduce the actual exhaust pressure. Under the influence of the reduced compressor speed, the opening control of the high-pressure side heating throttling valve needs to be weakened. Specifically, the closer the actual outlet air temperature is to the target outlet air temperature range, and the higher it is, the closer the compressor speed reduction is to the steady-state speed. At this point, the impact on the high-pressure side heating throttling valve is weakened, and the further the actual outlet air temperature is from the target outlet air temperature range, the greater the α... H Gradually decrease; conversely, the closer the actual outlet air temperature is to the target outlet air temperature range, the greater α becomes. H Gradually increase until it approaches 1. For example, at this point, 0 ≤ α H ≤1, as ΔT increases, the influence of compressor speed on the opening adjustment of the heating throttling valve on the high-pressure side weakens, α H It can show a trend of increasing to approach 1.

[0044] In some embodiments, when ΔT2 < ΔT < ΔT3, the actual outlet air temperature falls within the target outlet air temperature fluctuation range, and the compressor speed is basically in a steady state. At this time, the impact on the high-pressure side is smaller, and the heating throttling valve on the high-pressure side can adjust normally according to the given speed. In this case, α H If it approaches 1, it can show a trend of remaining unchanged.

[0045] In some embodiments, 0 < ΔT3 ≤ ΔT ≤ ΔT4, the closer the actual outlet air temperature is to the target outlet air temperature range and the smaller it is, the closer the compressor speed increases to the steady-state speed. At this point, the impact on the high-pressure side gradually weakens, and the adjustment of the high-pressure side relies more on the heating throttling valve. Furthermore, an increase in compressor speed will cause an increase in actual discharge pressure. Because the actual discharge pressure is higher at this time, the heating throttling valve itself needs to increase its opening to reduce the actual discharge pressure. Therefore, under the influence of the increased compressor speed, it is necessary to strengthen the opening control of the heating throttling valve on the high-pressure side. That is, the further the actual outlet air temperature is from the target outlet air temperature range, the greater the α... H Gradually increase; conversely, the closer the actual outlet air temperature is to the target outlet air temperature, the smaller the impact of compressor speed on the adjustment of the heating throttling valve opening. H Gradually decrease until it approaches 1, for example: at this point, 1≤α H ≤max, where max>1, as ΔT increases, α H It may show an increasing trend.

[0046] In some embodiments, when ΔT > ΔT4 > 0, and the actual outlet air temperature is much lower than the target outlet air temperature range, the compressor speed needs to continue to increase, which has a significant impact on the increase in high pressure on the high-pressure side. Since the actual exhaust pressure is greater than the target exhaust pressure + ΔQ at this time, the heating throttling valve itself needs to open wider to reduce pressure. Considering the positive correlation between the increase in compressor speed and the increase in pressure, it is necessary to strengthen the control of the opening degree of the heating throttling valve on the high-pressure side. For example, at this time α H It is equal to or close to max, where max > 1, and as ΔT increases, α H It can exhibit a trend that remains unchanged.

[0047] By adopting the above-mentioned regulation method based on the first influencing factor, it is possible to reduce the situation where the control pressure of the heating throttling valve is adjusted too quickly in the early stage, and the opening of the heating throttling valve is too small in the later stage after the compressor speed increases.

[0048] Please see Figure 3 In some embodiments, the step of determining the first influencing factor by selecting operation one, operation two, or operation three based on the relationship between the actual exhaust pressure and the target exhaust pressure includes: when the target exhaust pressure - ΔQ ≤ the actual exhaust pressure ≤ the target exhaust pressure + ΔQ, operation three is selected. In this case, as ΔT increases, α HIt can exhibit a trend of remaining unchanged, where △Q≥0; in some specific embodiments, when operation three is performed, α H =1.

[0049] In some embodiments, when the target exhaust pressure - ΔQ ≤ the actual exhaust pressure ≤ the target exhaust pressure + ΔQ, it indicates that the exhaust pressure has reached a steady state within the fluctuation range of the target exhaust pressure. At this time, the heating throttling valve on the high-pressure side can adjust normally at a given speed. At this time, α H If it approaches 1, it can show a trend of remaining unchanged.

[0050] Please see Figure 4 In some embodiments, the steps of the thermal management system control method further include: determining a second influencing factor based on the target evaporator temperature, the actual evaporator temperature, the actual exhaust pressure, and the target exhaust pressure, and adjusting the opening of the evaporator throttle valve based on the second influencing factor and the opening increment value of the evaporator throttle valve in the current cycle.

[0051] Please see Figure 5 In some embodiments, the determination of the second influencing factor includes obtaining the target evaporator temperature and the actual evaporator temperature.

[0052] In some embodiments, the step of regulating the opening of the evaporator throttle valve based on the second influencing factor and the current cycle evaporator throttle valve opening increment includes: the relationship between the second influencing factor and the evaporator throttle valve opening satisfies:

[0053] u L (n)=u L (n-1)+△u L (n)*α L

[0054] Among them, u L (n) represents the current cycle evaporator throttle valve opening output value, u L (n-1) represents the evaporator throttle valve opening output value from the previous cycle, Δu L (n) represents the current cycle evaporator throttle valve opening increment, α L It is the second most influential factor.

[0055] In a specific embodiment, the second influencing factor, also known as the system low-pressure side influencing factor, is used to regulate the opening degree of the evaporator throttle valve on the low-pressure side. Regulating the evaporator throttle valve opening degree based on the second influencing factor and the current cycle's evaporator throttle valve opening increment reduces the time and cost associated with extensive calibration and mitigates the problem of not being able to exhaustively account for multiple operating conditions.

[0056] Among them, the second influencing factor ≥0 indicates the influence on the evaporator throttle valve adjustment rate, ΔuL (n) represents increment values ​​with positive and negative values. The second influence factor uses 1 as a balance point; the further it is from 1, the greater the influence. When the second influence factor is greater than 1, it correlates with the execution rate Δu. L Multiplying (n) will increase the adjustment rate of the evaporator throttle valve, indicating that the evaporator throttle valve needs to perform faster adjustment; when the second influence factor is less than 1, it is related to the execution rate Δu L After multiplying by (n), the adjustment rate of the evaporator throttle valve will be suppressed, and the adjustment of the evaporator throttle valve will be further slowed down.

[0057] In some embodiments, the step of determining the second influencing factor based on the target evaporator temperature, the actual evaporator temperature, the actual exhaust pressure, and the target exhaust pressure includes: selecting to perform operation four, operation five, or operation six to determine the second influencing factor based on the relationship between the target evaporator temperature and the actual evaporator temperature.

[0058] Operation four is that as ΔP increases, α L Decrease or remain unchanged;

[0059] Operation 5 is that as ΔP increases, α L Increase or remain unchanged;

[0060] Operation six is ​​that as ΔP increases, α L Remain unchanged;

[0061] Where △P equals the target exhaust pressure minus the actual exhaust pressure.

[0062] In some embodiments, a second influencing factor is determined based on the target evaporator temperature, the actual evaporator temperature, the actual exhaust pressure, and the target exhaust pressure. Since the actual exhaust pressure is related to the opening degree of the heating throttle valve on the high-pressure side and the compressor speed, it can take into account the influence of the compressor speed and the opening degree of the heating throttle valve on the low-pressure side and the temperature, thereby improving the control accuracy of the evaporator throttle valve.

[0063] Please see Figure 6 In some embodiments, based on the relationship between the target evaporator temperature and the actual evaporator temperature, the step of determining the second influencing factor by performing operation four, operation five, or operation six is ​​selected, including:

[0064] In some embodiments, when the actual evaporator temperature > the target evaporator temperature + ΔR, operation four is performed. In this case, as ΔP increases, α... L Decrease or remain unchanged, where ΔR ≥ 0; in some specific embodiments, when operation four is performed and ΔP ≥ 0, 0 ≤ α L ≤1; When operation four is executed and ΔP < 0, α L ≥1.

[0065] In some embodiments, denoted as △P1<△P2<0<△P3<△P4, the evaporator throttling valve is regulated in the following manner:

[0066] In some embodiments, when ΔP < ΔP1 < 0, and the actual exhaust pressure far exceeds the target exhaust pressure, the opening of the heating throttling valve needs to be significantly increased. This causes a drop in high pressure on the high-pressure side, leading to a significant increase in the evaporator temperature on the low-pressure side, thus significantly increasing the impact on the evaporator temperature. Because the evaporator temperature is too high at this time, the opening of the evaporator throttling valve needs to be reduced to lower the evaporator temperature. Under the influence of the high-pressure side, the evaporator throttling valve needs to adjust more quickly to compensate for this, preventing the evaporator temperature from rising excessively. For example: at this time, α... L =max, where max>1, as ΔP increases, α L It can exhibit a trend that remains unchanged.

[0067] In some embodiments, when ΔP1≤ΔP≤ΔP2<0, the actual exhaust pressure exceeds the target exhaust pressure, requiring an increase in the opening of the heating throttle valve. This causes the evaporator temperature on the low-pressure side to rise. Since the evaporator temperature is high at this time, the opening of the evaporator throttle valve needs to be reduced to lower the evaporator temperature. Under the influence of the high-pressure side, the adjustment of the evaporator throttle valve opening needs to be accelerated. When the actual exhaust pressure approaches the target exhaust pressure, the influence of the heating throttle valve on the low-pressure side weakens. The further the actual exhaust pressure is from the target exhaust pressure, the greater the influence on the high-pressure side. L The larger the value, the faster the evaporator throttle valve adjusts. For example, in this case, 1≤α L ≤max, where max>1, as ΔP increases, the actual exhaust pressure gets closer to the target exhaust pressure, α L It shows a trend of gradually decreasing.

[0068] In some embodiments, when ΔP2 < ΔP < ΔP3, the actual exhaust pressure falls within the target exhaust pressure range, and the evaporator throttle valve on the low-pressure side can adjust normally according to the given speed. For example: at this time, α L As ΔP increases, α approaches 1. L It can exhibit a trend that remains unchanged.

[0069] In some embodiments, when 0 < ΔP3 ≤ ΔP ≤ ΔP4, the actual exhaust pressure is close to the target exhaust pressure and is relatively small. The heating throttling valve needs to reduce its opening, and its adjustment range slows down, resulting in a decrease in evaporator temperature. At this time, the impact on the low-pressure side gradually weakens. Since the evaporator temperature is relatively high at this time, the evaporator throttling valve opening needs to be reduced to lower the evaporator temperature. Under the influence of the high-pressure side, the adjustment rate of the evaporator throttling valve can be reduced. At this point, the further the actual exhaust pressure is from the target exhaust pressure, the greater the impact on the high-pressure side.L The smaller. For example, in this case, 0 ≤ α L ≤1, as ΔP increases, the influence of the high-pressure side increases, α L It can show a trend of gradually decreasing.

[0070] In some embodiments, when ΔP > ΔP4 > 0, the actual exhaust pressure is much lower than the target exhaust pressure. The heating throttling valve needs to adjust the high-pressure side to increase pressure, significantly reducing the opening, causing a decrease in evaporator temperature. This also has a significant impact on the low-pressure reduction. Since the evaporator temperature is high at this time, the opening of the evaporator throttling valve needs to be reduced to lower the evaporator temperature. At this time, under the influence of the high-pressure side, to ensure the single controllability of the variable, the adjustment of the evaporator throttling valve opening is weakened. For example: at this time, α L α is equal to or close to 0, and as ΔP increases, α L It can exhibit a trend that remains unchanged.

[0071] In some embodiments, when the actual evaporator temperature is less than the target evaporator temperature - ΔR, operation five is performed. In this case, as ΔP increases, α... L Increase or remain unchanged; in some specific embodiments, when operation five is performed and ΔP≥0 is satisfied, α L ≥1; When operation five is executed and ΔP < 0, 0 ≤ α L ≤1.

[0072] In some embodiments, denoted as △P1<△P2<0<△P3<△P4, the evaporator throttling valve is regulated in the following manner:

[0073] In some embodiments, when ΔP < ΔP1 < 0, and the actual exhaust pressure far exceeds the target exhaust pressure, the opening of the heating throttle valve needs to be significantly increased. The decrease in high pressure causes a significant increase in evaporator temperature. Since the evaporator temperature is low at this time, the opening of the evaporator throttle valve needs to be increased to raise the evaporator temperature. Under the influence of the high-pressure side, the adjustment rate of the evaporator throttle valve's opening can be weakened. For example: at this time, α L α is equal to or close to 0, and as ΔP increases, α L It can exhibit a trend that remains unchanged.

[0074] In some embodiments, when ΔP1≤ΔP≤ΔP2<0, the actual exhaust pressure is close to the target exhaust pressure range and is relatively high. In this case, the heating throttle valve needs to increase its opening to reduce the high-pressure pressure, which will cause the evaporator temperature to rise. Since the evaporator temperature is low at this time, the evaporator throttle valve opening needs to be increased to raise the evaporator temperature. Under the influence of the high-pressure side, the opening adjustment of the evaporator throttle valve itself needs to be reduced to compensate for this. Furthermore, the closer the actual exhaust pressure is to the target exhaust pressure, the smaller the influence of the high-pressure side on the low-pressure side.L The larger the value, the closer it tends to 1, meaning it relies more on the opening of the evaporator throttle valve itself for adjustment; for example, in this case, 0 ≤ α. L ≤1, as ΔP increases, α L It can show a gradually increasing trend.

[0075] In some embodiments, when ΔP2 < ΔP < ΔP3, the actual exhaust pressure falls within the target exhaust pressure range, the influence of the high-pressure side on the low-pressure side is weakened, and the evaporator throttle valve on the low-pressure side can adjust normally according to the given speed. For example: at this time, α L As ΔP increases, α approaches 1. L It can exhibit a trend that remains unchanged.

[0076] In some embodiments, when 0 < ΔP3 ≤ ΔP ≤ ΔP4, the actual exhaust pressure is close to the target exhaust pressure range and is relatively small. The heating throttling valve needs to reduce its opening, and its adjustment range slows down, causing a decrease in evaporator temperature. Since the evaporator temperature is low at this time, the evaporator throttling valve opening needs to be increased to raise the evaporator temperature. At this point, low-pressure regulation is more concentrated on the evaporator throttling valve. The closer the actual exhaust pressure is to the target exhaust pressure, the smaller the impact of the high-pressure side on the low-pressure side. L The smaller it is, the closer it approaches 1. For example, in this case, 1 ≤ α. L ≤max, where max>1, as ΔP increases, α L It can show a gradually increasing trend.

[0077] In some embodiments, when ΔP > ΔP4 > 0, and the actual exhaust pressure is much lower than the target exhaust pressure range, the opening of the heating throttling valve needs to be further reduced to lower the evaporator temperature. The high-pressure side also has a significant impact on the low-pressure side. Because the evaporator temperature is low at this time, the evaporator throttling valve needs to be opened wider. Under the influence of the high-pressure side, the opening adjustment of the evaporator throttling valve needs to be accelerated to compensate for this. For example: at this time, α L =max, where max>1, as ΔP increases, α L It can exhibit a trend that remains unchanged.

[0078] In some embodiments, when the target evaporator temperature - ΔR ≤ actual evaporator temperature ≤ target evaporator temperature + ΔR, operation six is ​​performed. In this case, as ΔP increases, α... L It remains unchanged, where ΔR ≥ 0; in some specific embodiments, when operation six is ​​performed, α L =1.

[0079] In some embodiments, when the target evaporator temperature - ΔR ≤ actual evaporator temperature ≤ target evaporator temperature + ΔR, it indicates that the evaporator temperature has reached a steady state within the fluctuation range of the target evaporator temperature. At this time, the evaporator throttling valve on the low-pressure side can adjust normally according to the given speed. At this time, α L It tends to 1 and remains unchanged.

[0080] By adopting the above-mentioned method of regulation based on the second influencing factor, the phenomenon of the evaporator throttling valve opening being reduced in the early stage to approach the evaporator temperature, and then opening too large again in the later stage when the evaporator temperature is too low, can be reduced.

[0081] In some embodiments, the target outlet air temperature and the target evaporator temperature are calculated based on a vehicle heat load model. The vehicle heat load model refers to the heat load required at a given moment to maintain a set temperature under specific operating conditions within a given time period. In some embodiments, the target exhaust pressure is determined based on the outlet temperature of the outdoor heat exchanger, the evaporator temperature, and a simulation model, wherein the target exhaust pressure is the optimal pressure of the system.

[0082] In some embodiments, the compressor speed of the thermal management system is controlled by PID calculation based on the difference between the target outlet air temperature and the actual outlet air temperature. In a specific embodiment, a PID controller is used to regulate the compressor speed.

[0083] In some embodiments, the thermal management system of this application operates as follows:

[0084] When the thermal management system is in shutdown mode, the compressor stops, and the heating expansion valve (HeatEXV) and evaporator expansion valve (AcEXV) are in their default opening positions. The default opening position is generally in the middle position, which is intended to allow the thermal management system to quickly approach a stable state when running in dehumidification and heating mode.

[0085] After the thermal management system is started and the compressor runs, the heating throttling valve (HeatEXV) and the evaporator throttling valve (AcEXV) are adjusted using PID control based on their current opening degrees. In some embodiments, incremental PID is used, where u(n) = u(n-1) + Δu(n) * α, where u(n) is the current cycle throttling valve opening output value, u(n-1) is the previous cycle throttling valve opening output value, Δu(n) is the current cycle throttling valve opening increment, and α is the influencing factor. The influencing factor of the system is monitored in real time, and the calculation is performed based on the relationship between the actual value and the target value. The compressor, heating throttling valve, and evaporator throttling valve operate synchronously to ensure rapid adjustment.

[0086] After the compressor starts operating, it first changes the high and low pressure states of the system and the outlet air temperature. Simultaneously, the opening of the throttle valve further adjusts, also affecting the high-pressure and low-pressure sides of the system, as well as the outlet air temperature. In a multi-objective, multi-coupling control system, this application prioritizes using the compressor that initially changes the system state as the starting point.

[0087] Among them, the impact factors (first impact factor and second impact factor) are newly added variables, taking values ​​≥0, indicating the influence on the adjustment rate of other components. The impact factors use 1 as a balance point; the further away from 1, the greater the impact. When the impact factor is greater than 1, multiplying it by the execution rate will enhance the adjustment rate, indicating a need for faster adjustment; when the impact factor is less than 1, multiplying it by the execution rate will suppress the adjustment rate, further slowing down the adjustment of the execution components.

[0088] In some embodiments, when the compressor speed is limited by discharge temperature, discharge pressure, and suction pressure, there is not much room for a significant increase. Therefore, the first influencing factor α is... H The value is 1. That is, when any one of the following conditions is met: current exhaust temperature > intake pressure limit, current exhaust pressure > intake pressure limit, or current intake pressure > intake pressure limit, the compressor speed will not have significant room for increase, reducing the impact on the high-pressure side. The adjustment of the high-pressure side pressure mainly relies on the heating throttling valve itself. At this time, the first influencing factor α... H It tends to 1. Among them, the current exhaust temperature, current exhaust pressure, and current intake pressure are acquired by sensors.

[0089] Please see Figure 7 In some embodiments, this application also provides a thermal management system control device 10, including an acquisition module 11, a determination module 12, and a control module 13. The determination module 12 is used to determine a first influencing factor based on the actual exhaust pressure, the target exhaust pressure, the target air outlet temperature, and the actual air outlet temperature. The control module 13 is used to regulate the opening degree of the heating throttling valve based on the first influencing factor and the opening degree increment value of the heating throttling valve in the current cycle.

[0090] In some embodiments, the thermal management system control device 10 further includes a thermal management system control device 10, comprising an acquisition module 11 for acquiring actual exhaust pressure, target exhaust pressure, target outlet air temperature and actual outlet air temperature.

[0091] The thermal management system control device provided in this application acquires the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature through the acquisition module 11. The determination module 11 determines the first influencing factor based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature, and actual outlet air temperature. The control module 13 adjusts the opening of the heating throttling valve based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle. This can take into account the influence of compressor speed changes on high-pressure side pressure when controlling the actual outlet air temperature, and make the control of the heating throttling valve more precise.

[0092] Please see Figure 8 In some embodiments, this application also provides a thermal management system control device 20, including a processor 21, a memory 22, and a thermal management system control program stored in the memory 22 and executable by the processor, wherein when the thermal management system control program is executed by the processor 21, it implements the steps of the above-described thermal management system control method.

[0093] The thermal management system control device provided in this application, when the thermal management system control program is executed by the processor 21, determines a first influencing factor based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature and actual outlet air temperature, and adjusts the opening of the heating throttling valve based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle, which can take into account the influence of compressor speed change on high-pressure side pressure when controlling actual outlet air temperature, and make the control of the heating throttling valve more precise.

[0094] Although this application has been described in detail with reference to the above embodiments, those skilled in the art should understand that modifications or equivalent substitutions can still be made to this application, and all technical solutions and improvements that do not depart from the spirit and scope of this application should be covered within this application.

Claims

1. A control method for a thermal management system, characterized in that, The first influencing factor is determined based on the actual exhaust pressure, target exhaust pressure, target air outlet temperature, and actual air outlet temperature. The opening of the heating throttling valve is then adjusted based on the first influencing factor and the current cycle heating throttling valve opening increment.

2. The thermal management system control method according to claim 1, characterized in that, The step of regulating the opening of the heating throttle valve based on the first influencing factor and the current cycle heating throttle valve opening increment includes: the relationship between the first influencing factor and the heating throttle valve opening satisfies: u H (n)=u H (n-1)+△u H (n)*α H Among them, u H (n) represents the current cycle heating throttle valve opening output value, u H (n-1) represents the output value of the heating throttling valve opening in the previous cycle, Δu H (n) represents the increment of the opening of the heating throttling valve in the current cycle, α H It is the number one impact factor.

3. The thermal management system control method according to claim 2, characterized in that, The step of determining the first influencing factor based on the actual exhaust pressure, target exhaust pressure, target outlet air temperature and actual outlet air temperature includes: based on the relationship between the actual exhaust pressure and the target exhaust pressure, selecting to perform operation one, operation two or operation three to determine the first influencing factor; The first operation is that as ΔT increases, α... H Decrease or remain unchanged; The second operation is that as ΔT increases, α H Increase or remain unchanged; The third operation is that as ΔT increases, α H Remain unchanged; Wherein, △T is equal to the target outlet air temperature minus the actual outlet air temperature.

4. The thermal management system control method according to claim 3, characterized in that, The step of determining the first influencing factor by selecting to execute operation one, operation two or operation three based on the relationship between the actual exhaust pressure and the target exhaust pressure includes: when the actual exhaust pressure < the target exhaust pressure - ΔQ, operation one is selected, where ΔQ ≥ 0; When operation one is performed, and ΔT≥0 is satisfied, 0≤α H ≤1; When operation one is executed and ΔT < 0, α H ≥1.

5. The thermal management system control method according to claim 3, characterized in that, The step of determining the first influencing factor by selecting to execute operation one, operation two or operation three based on the relationship between the actual exhaust pressure and the target exhaust pressure includes: when the actual exhaust pressure > the target exhaust pressure + ΔQ, selecting to execute operation two, where ΔQ ≥ 0; When operation two is performed, and ΔT≥0 is satisfied, α H ≥1; When operation two is executed and ΔT < 0, 0 ≤ α H ≤1.

6. The thermal management system control method according to claim 3, characterized in that, The step of determining the first influencing factor based on the relationship between the actual exhaust pressure and the target exhaust pressure, selecting to execute operation one, operation two, or operation three, includes: when the target exhaust pressure - ΔQ ≤ the actual exhaust pressure ≤ the target exhaust pressure + ΔQ, selecting to execute operation three, where ΔQ ≥ 0; when executing operation three, α H =1.

7. The thermal management system control method according to claim 1, characterized in that, The steps of the thermal management system control method further include: determining a second influencing factor based on the target evaporator temperature, the actual evaporator temperature, the actual exhaust pressure, and the target exhaust pressure; and adjusting the opening of the evaporator throttle valve based on the second influencing factor and the opening increment value of the evaporator throttle valve in the current cycle.

8. The thermal management system control method according to claim 7, characterized in that, The step of regulating the opening of the evaporator throttle valve based on the second influencing factor and the current cycle evaporator throttle valve opening increment includes: the relationship between the second influencing factor and the evaporator throttle valve opening satisfies: u L (n)=u L (n-1)+△u L (n)*α L Among them, u L (n) represents the current cycle evaporator throttle valve opening output value, u L (n-1) represents the evaporator throttle valve opening output value from the previous cycle, Δu L (n) represents the current cycle evaporator throttle valve opening increment, α L It is the second most influential factor.

9. The thermal management system control method according to claim 8, characterized in that, The step of determining the second influencing factor based on the target evaporator temperature, the actual evaporator temperature, the actual exhaust pressure, and the target exhaust pressure includes: selecting to perform operation four, operation five, or operation six to determine the second influencing factor based on the relationship between the target evaporator temperature and the actual evaporator temperature; The fourth operation is that as ΔP increases, α... L Decrease or remain unchanged; The fifth operation is that as ΔP increases, α... L Increase or remain unchanged; The sixth operation is that as ΔP increases, α... L Remain unchanged; Wherein, △P is equal to the target exhaust pressure minus the actual exhaust pressure.

10. The thermal management system control method according to claim 1, characterized in that, The step of determining the second influencing factor based on the relationship between the target evaporator temperature and the actual evaporator temperature, by selecting to perform operation four, operation five, or operation six, includes: When the actual evaporator temperature > the target evaporator temperature + ΔR, select to execute operation four, where ΔR ≥ 0; when executing operation four and satisfying ΔP ≥ 0, 0 ≤ α L ≤1; When operation four is executed and ΔP < 0, α L ≥1; When the actual evaporator temperature is less than the target evaporator temperature - ΔR, select to execute operation five. When operation five is executed and ΔP ≥ 0, α L ≥1; When operation five is executed and ΔP < 0, 0 ≤ α L ≤1; When the target evaporator temperature - ΔR ≤ actual evaporator temperature ≤ target evaporator temperature + ΔR, select to execute operation six. When executing operation six, α L =1.

11. A thermal management system control device, characterized in that, It includes a determination module and a control module. The determination module is used to determine a first influencing factor based on the actual exhaust pressure, the target exhaust pressure, the target air outlet temperature, and the actual air outlet temperature. The control module is used to adjust the opening of the heating throttling valve based on the first influencing factor and the opening increment value of the heating throttling valve in the current cycle.

12. A thermal management system control device, characterized in that, The system includes a processor, a memory, and a thermal management system control program stored in the memory and executable by the processor, wherein when the thermal management system control program is executed by the processor, it implements the steps of the thermal management system control method as described in any one of claims 1 to 10.

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