Thermal management control method and system and vehicle

Abstract

The invention discloses a heat management control method and system and a vehicle. The method comprises the steps that a target heating temperature is obtained through calculation according to the heat source requirement in the vehicle, and a target refrigeration temperature is obtained through calculation according to the refrigeration requirement in the vehicle; wherein the target heating temperature is higher than the target refrigerating temperature; the rotating speed of a compressor is set according to the target heating temperature and the first real-time temperature in the first pipeline; the opening degree of a first electronic expansion valve is set according to the target refrigeration temperature and the first real-time pressure in the first pipeline; the heating and ventilation assembly is used for evaporating the liquid and generating gas, the second pipeline is used for supplying the gas to the second condensation assembly, and the second condensation assembly is used for carrying out secondary evaporation on the gas; and the opening degree of the second electronic expansion valve is set according to the second real-time pressure and the second real-time temperature in a third pipeline between the second condensation assembly and the compressor and the target superheat degree.

Description

Technical Field

[0001] The present application relates to the field of vehicle technology, and in particular to a thermal management control method, system and vehicle. Background Art

[0002] The dehumidification function of the vehicle has always had an energy consumption problem. When the outdoor temperature is low and the dehumidification function needs to be performed, the evaporator in the heating, ventilation and air conditioning (HVAC) components in the vehicle requires a lower cooling temperature, but the air conditioning and / or battery heating system in the vehicle requires a higher heating temperature. In the prior art, when the compressor meets the cooling temperature, the speed of the compressor can no longer be adjusted, so that the heat pump system cannot meet the heating temperature of the air conditioning and / or battery system, and the positive temperature coefficient (Positive Temperature Coefficient, PTC) heater needs to be turned on for heating operation to meet the heating temperature of the air conditioning and / or battery system. However, when using a PTC heater for heating operation, the energy consumption of the vehicle is too high, and the heating efficiency of the vehicle is low. Summary of the invention

[0003] In view of this, the present application provides a thermal management control method, system and vehicle, which can reduce energy consumption in the vehicle and improve the heating efficiency of the vehicle.

[0004] The present application is introduced below from different aspects. It should be understood that the implementation methods and beneficial effects of the following different aspects can be referenced to each other.

[0005] In a first aspect, the present application provides a thermal management control method, the thermal management control method comprising: The target heating temperature is calculated according to the heat source demand in the vehicle, and the target cooling temperature is calculated according to the cooling demand in the vehicle; wherein the target heating temperature is greater than the target cooling temperature; The speed of the compressor is set according to the target heating temperature and the first real-time temperature in the first pipeline; wherein the first pipeline connects the first condensing component and the HVAC component; setting the opening of the first electronic expansion valve according to the target refrigeration temperature and the first real-time pressure in the first pipeline; Using the HVAC component to evaporate the liquid and generate gas, using a second pipeline to provide the gas to a second condensation component, and using the second condensation component to evaporate the gas for a second time; and The opening degree of the second electronic expansion valve is set according to the second real-time pressure and the second real-time temperature in the third pipeline between the second condensing component and the compressor and the target superheat degree.

[0006] According to the embodiment of the present application, when there is a heating demand and a cooling demand at the same time and the target heating temperature is greater than the target cooling temperature, the gas generated by the HVAC component is provided to the second condensing component by setting a second pipeline, and the gas is evaporated twice by the second condensing component. Compared with the PTC heating method, the heating efficiency of the secondary evaporation method is greater than the heating efficiency of the PTC heater in the traditional technology, thereby improving the heating efficiency of the vehicle and achieving energy saving. At the same time, the opening of the second electronic expansion valve performs PID feedback control, which can optimize the performance of the thermal management control system.

[0007] In combination with the first aspect, in a possible implementation, the step of setting the opening of the second electronic expansion valve according to the second real-time pressure and the second real-time temperature in the third pipeline and the target superheat further includes: calculating the actual superheat of the gas entering the compressor according to the second real-time pressure in the third pipeline and the second real-time temperature; and The opening degree of the second electronic expansion valve is set according to the actual superheat degree and the target superheat degree.

[0008] In combination with the first aspect, in a possible implementation manner, the rotation speed of the compressor is calculated according to the following formula: ,in, is the speed of the compressor, is the first proportionality coefficient, is the first integral coefficient, is the difference between the target heating temperature and the first real-time temperature.

[0009] In combination with the first aspect, in a possible implementation manner, the opening degree of the first electronic expansion valve is calculated using the following formula: ,in, is the opening degree of the first electronic expansion valve, is the second proportional coefficient, Δ2 is the difference between the target pressure and the first real-time pressure, is the second integral coefficient.

[0010] In combination with the first aspect, in a possible implementation manner, the actual superheat is calculated according to the following formula: ,in, is the actual superheat, is the second real-time temperature in the third pipeline, is the pressure-saturation temperature function corresponding to the first condensation component.

[0011] In combination with the first aspect, in a possible implementation manner, the opening degree of the second electronic expansion valve is calculated using the following formula: ,in, is the opening percentage of the second electronic expansion valve, is the third proportionality coefficient, is the actual superheat, is the third integral coefficient, is the target superheat.

[0012] In combination with the first aspect, in a possible implementation, the first electronic expansion valve is arranged on the first pipeline and is arranged close to the HVAC component; the third pipeline connects the second condensing component and the compressor, and the second electronic expansion valve is arranged on the third pipeline and is arranged close to the compressor.

[0013] In a second aspect, the present application provides a thermal management control system, the thermal management control system comprising: A compressor, configured to set a speed of the compressor according to a target heating temperature calculated based on a heat source demand in the vehicle and a first real-time temperature in a first pipeline; wherein the first pipeline connects a first condensing component and a HVAC component; A first electronic expansion valve, used to set its corresponding opening degree according to a target cooling temperature calculated according to a cooling demand in the vehicle and a first real-time pressure in the first pipeline; HVAC components for evaporating liquids to form gases; A second condensing component is used to receive the gas provided by the HVAC component through a second pipeline and perform secondary evaporation; The second electronic expansion valve is used to set its corresponding opening degree according to the second real-time pressure and the second real-time temperature in the third pipeline between the second condensing component and the compressor and the target superheat.

[0014] In combination with the second aspect, in a possible implementation, the thermal management control system also includes a first sensor and a second sensor; the first sensor is arranged on the first pipeline and is arranged close to the HVAC component; the first sensor is used to sense the first real-time pressure in the first pipeline; the second sensor is arranged on the third pipeline and is arranged close to the compressor; the second sensor is used to sense the second real-time pressure and the second real-time temperature in the third pipeline.

[0015] In a third aspect, the present application provides a vehicle comprising a processor and a memory, wherein the memory is used to store a plurality of program instructions, and when the processor calls the program instructions, the above-mentioned thermal management control method can be implemented.

[0016] Compared with the prior art, this application has the following advantages: 1. In the embodiments of the present application, when there are both heating demand and cooling demand and the target heating temperature is greater than the target cooling temperature, the gas generated by the HVAC component is provided to the second condensing component by setting a second pipeline, and the gas is evaporated secondary by the second condensing component. Compared with the PTC heating method, the heating efficiency of the secondary evaporation method is greater than the heating efficiency of the PTC heater in the traditional technology, thereby improving the heating efficiency of the vehicle and achieving energy-saving effects.

[0017] 2. In an embodiment of the present application, the opening of the second electronic expansion valve is set according to the second real-time pressure and the second real-time temperature in the second pipeline and the target superheat of the compressor to implement PID feedback control, thereby optimizing the performance of the thermal management control system. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0019] Figure 1 A flow chart of a thermal management control method provided in an embodiment of the present application.

[0020] Figure 2 for Figure 1 Detailed flowchart of step S15 in FIG.

[0021] Figure 3 A schematic diagram of an application scenario of a thermal management control system provided in an embodiment of the present application.

[0022] Figure 4 A schematic diagram of the modules of a vehicle provided in an embodiment of the present application.

[0023] Main component symbols Steps S11-S15, S151-S152 Vehicle 100 Thermal management control system1 Battery heating control system 2 Air conditioning control system 3 Compressor 10 First condensation assembly 20 First electronic expansion valve 30 HVAC components 40 Second condensation assembly 50 Second electronic expansion valve 60 First sensor 70 Second sensor 80 Processor 4 Memory 5 Communication interface 6 The following specific implementation methods will further illustrate the present application in conjunction with the above-mentioned drawings. DETAILED DESCRIPTION

[0024] In order to enable those skilled in the art to better understand the solution of the present application, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of the present application.

[0025] In the description of the present application, it should be understood that the terms "first", "second", "third", "fourth" and "fifth" etc. are used to distinguish different objects rather than to describe a specific order.

[0026] In the description of this application, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, an electrical connection, or mutual communication; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0027] The term "comprises" and any variations thereof are intended to cover non-exclusive inclusions. For example, a process, method, system, product, or device that includes a series of steps or modules is not limited to the listed steps or modules, but may optionally include steps or modules that are not listed, or may optionally include other steps or modules that are inherent to these processes, methods, products, or devices.

[0028] See also Figure 1 , which is a flow chart of a thermal management control method of at least one embodiment of the present application. In at least one embodiment of the present invention, the thermal management control method is applied to a vehicle 100 (such as Figure 4 As shown in FIG. 1 , it can be understood that the vehicle 100 includes a thermal management control system 1. Figure 3As shown, the thermal management control system 1 includes a compressor 10, a first condensing component 20, a first electronic expansion valve 30, a HVAC component 40, a second condensing component 50, a second electronic expansion valve 60, a first sensor 70, and a second sensor 80. In at least one embodiment of the present application, the HVAC component 40 is a heating, ventilation and air conditioning (HVAC) component.

[0029] The thermal management control method comprises the following steps: In step S11 , a target heating temperature is calculated according to a heating demand in the vehicle 100 , and a target cooling temperature is calculated according to a cooling demand in the vehicle 100 .

[0030] In at least one embodiment of the present application, the target heating temperature is greater than the target cooling temperature. The heating demand includes the battery heating control system 2 in the vehicle 100 (such as Figure 4 The first heating temperature corresponding to the battery preheating function of the vehicle 100 (as shown) and the air conditioning control system 3 in the vehicle 100 (as shown) Figure 4 The second heating temperature corresponding to the heating function of the vehicle 100 (as shown), and the higher of the two temperatures is used as the target heating temperature. That is, when the first heating temperature is greater than the second heating temperature, the first heating temperature is set as the target heating temperature; when the first heating temperature is less than or equal to the second heating temperature, the second heating temperature is set as the target heating temperature. Among them, the first heating temperature is the temperature at which the battery in the vehicle 100 is at its best performance; the second heating temperature can be set according to the user's operation. The cooling demand is the target cooling temperature calculated based on the difference between the real-time temperature outside the vehicle 100 and the predetermined temperature. That is, the target cooling temperature is a predetermined temperature difference lower than the real-time temperature. In at least one embodiment of the present application, the predetermined temperature difference corresponding to the dehumidification function of the air-conditioning control system 3 in the vehicle 100 is 3°C, but it is not limited thereto. In other embodiments, the predetermined temperature difference can also be adjusted according to demand, and the specific value is not specifically limited here.

[0031] Step S12 , setting the rotation speed of the compressor 10 according to the target heating temperature and the first real-time temperature in the first pipeline 101 .

[0032] In at least one embodiment of the present application, the first pipeline 101 connects the first condensing component 20 and the HVAC component 40. The refrigerant enters the HVAC component 40 through the first pipeline 101 and realizes the first evaporation on the evaporator in the HVAC component 40. The first real-time temperature is sensed by a sensor (not shown) disposed at the liquid outlet of the first condensing component 20. The speed of the compressor 10 can be feedback-controlled using proportional-integral-derivative (PID). Specifically, the speed of the compressor 10 is calculated by the following formula 1.

[0033] Formula 1 in, is the rotation speed of the compressor 10, is the first proportionality coefficient, is the first integral coefficient, is the difference between the target heating temperature and the first real-time temperature. In at least one embodiment of the present application, the first proportional coefficient is 0.1 and the first integral coefficient is 0.01, but is not limited thereto. In other embodiments, the specific values ​​of the first proportional coefficient and the first integral coefficient can be adjusted according to demand, and are not specifically limited here.

[0034] Step S13 , setting the opening of the first electronic expansion valve 30 according to the target cooling temperature and the first real-time pressure in the first pipeline 101 .

[0035] In at least one embodiment of the present application, the first electronic expansion valve 30 is disposed on the first pipeline 101 and is close to the air inlet of the HVAC component 40. The first real-time pressure is sensed by the first sensor 70. The opening of the first electronic expansion valve 30 can be calculated using a PID algorithm. Specifically, the opening of the first electronic expansion valve 30 can be calculated using the following formula 2.

[0036] Formula 2 in, is the opening percentage of the first electronic expansion valve 30, is the second proportional coefficient, Δ2 is the difference between the target pressure value and the current pressure value, Is the second integral coefficient. In at least one embodiment of the present application, the second proportional coefficient is 0.1, and the second integral coefficient is 0.05, but it is not limited thereto. In other embodiments, the specific values ​​of the second proportional coefficient and the second integral coefficient can be adjusted as needed, and are not specifically limited here. In at least one embodiment of the present application, a comparison table of the saturated evaporation temperature and pressure of at least one refrigerant is usually stored in the vehicle 100, and the target pressure value can be obtained by looking up the table according to the target refrigeration temperature. The target pressure value is related to the type of refrigerant in the first condensing component 20 and the target refrigeration temperature. In at least one embodiment of the present application, the refrigerant in the first condensing component 20 can be R134a, but it is not limited thereto.

[0037] Step S14, using the HVAC component 40 to evaporate the liquid and generate gas, using the second pipeline 102 to provide the gas to the second condensation component 50, and using the second condensation component 50 to evaporate the gas for a second time.

[0038] In at least one embodiment of the present application, the second pipeline 102 connects the HVAC component 40 and the second condensing component 50. The HVAC component 40 simultaneously provides both gas and liquid forms to the second condensing component 50 through the second pipeline 102. The second condensing component 50 absorbs heat from the air outside the vehicle 100 to perform secondary evaporation of the gas.

[0039] Step S15, setting the opening degree of the second electronic expansion valve 60 according to the second real-time pressure and the second real-time temperature in the third pipeline 103 and the target superheat degree.

[0040] In at least one embodiment of the present application, the second electronic expansion valve 60 is arranged on the second pipeline 103 and is close to the air outlet of the HVAC component 40; the third pipeline 103 connects the HVAC component 40 and the second condensing component 50. The first pipeline 101, the second pipeline 102 and the third pipeline 103 are not connected to each other. There are two forms of gas and liquid in the third pipeline 103. The second real-time pressure is sensed by the second sensor 80 arranged on the third pipeline 103 and close to the air inlet of the compressor 10. Among them, the second sensor 80 is a pressure and temperature sensor, which can sense the second real-time pressure and the second real-time temperature in the second pipeline 102. The target superheat is the temperature of the gas entering the compressor 10 that exceeds its saturation temperature, and is a fixed value. In at least one embodiment of the present application, the target superheat is 5°C.

[0041] Please also read Figure 2 , which is a detailed flow chart of step S15. Specifically, step S15 further includes the following steps: Step S151 , calculating the actual superheat of the gas entering the compressor 10 according to the second real-time pressure and the second real-time temperature in the third pipeline 103 .

[0042] In at least one embodiment of the present application, the actual superheat degree can be calculated by the following formula three.

[0043] Formula 3 in, is the actual superheat of the compressor 10, is the second real-time temperature, It is a pressure-saturation temperature function corresponding to the refrigerant type in the first condensing component 20.

[0044] Step S152, setting the opening degree of the second electronic expansion valve 60 according to the actual superheat degree and the target superheat degree.

[0045] In at least one embodiment of the present application, the opening degree of the second electronic expansion valve 60 can be calculated by the following formula 4.

[0046] Formula 4 in, is the opening percentage of the second electronic expansion valve 60, is the third proportionality coefficient, is the actual superheat of the compressor 10, is the third integral coefficient, is the target superheat. In at least one embodiment of the present application, the third proportional coefficient is 0.1 and the third integral coefficient is 0.05, but it is not limited thereto. In other embodiments, the specific values ​​of the second proportional coefficient and the third integral coefficient can be adjusted according to the needs, and are not specifically limited here.

[0047] Compared with the prior art, this application has the following advantages: 1. In the embodiment of the present application, when there are both heating demand and cooling demand and the target heating temperature is greater than the target cooling temperature, the gas generated by the HVAC component 40 is provided to the second condensing component 50 by setting the second pipeline 102, and the gas is evaporated secondary by the second condensing component 50. Compared with the PTC heating method, the heating efficiency of the secondary evaporation method is greater than the heating efficiency of the PTC heater in the traditional technology, thereby improving the heating efficiency of the vehicle 100 and achieving energy saving effect.

[0048] 2. In the embodiment of the present application, the opening of the second electronic expansion valve 60 is set according to the second real-time pressure and the second real-time temperature in the second pipeline 102 and the target superheat of the compressor 10 to implement PID feedback control, thereby optimizing the performance of the thermal management control system 1.

[0049] See also Figure 3 , which is a module diagram of a thermal management control system 1 of at least one embodiment of the present application. The thermal management control system 1 includes a compressor 10, a first condensing component 20, a first electronic expansion valve 30, a HVAC component 40, a second condensing component 50, a second electronic expansion valve 60, a first sensor 70, and a second sensor 80. In at least one embodiment of the present application, the HVAC component 40 is a heating, ventilation and air conditioning (HVAC) component.

[0050] The compressor 10 is used to generate high-pressure gas and provide it to the first condensing component 20. The speed of the compressor 10 can be PID feedback controlled according to the liquid temperature output by the first condensing component 20. In at least one embodiment of the present application, the speed of the compressor 10 can be calculated by the following formula 1.

[0051] Formula 1 Among them, according to is the rotation speed of the compressor 10, is the first proportionality coefficient, is the first integral coefficient, is the difference between the target heating temperature and the first real-time temperature. In at least one embodiment of the present application, the first proportional coefficient is 0.1 and the first integral coefficient is 0.01, but is not limited thereto. In other embodiments, the specific values ​​of the first proportional coefficient and the first integral coefficient can be adjusted according to demand, and are not specifically limited here.

[0052] The first condensing assembly 20 is connected to the HVAC assembly 40 through the first pipeline 101. The first condensing assembly 20 is used to cool the high-pressure gas to form a high-pressure liquid and provide it to the HVAC assembly 40. In at least one embodiment of the present application, the first condensing assembly 20 includes a liquid cooled condenser (LCC), and R134a is used as the refrigerant.

[0053] The first electronic expansion valve 30 is disposed on the first pipeline 101. The first electronic expansion valve 30 is used to reduce the pressure of the high-pressure liquid in the first pipeline 101 to form a low-pressure liquid and provide it to the HVAC component 40. The opening of the first electronic expansion valve 30 can be set according to the target cooling temperature and the first real-time pressure in the first pipeline 101. In at least one embodiment of the present application, the opening of the first electronic expansion valve 30 can be calculated by the following formula 2.

[0054] Formula 2 in, is the opening percentage of the first electronic expansion valve 30, is the second proportional coefficient, Δ2 is the difference between the target pressure value and the current pressure value, Is the second integral coefficient. In at least one embodiment of the present application, the second proportional coefficient is 0.1, and the second integral coefficient is 0.05, but it is not limited thereto. In other embodiments, the specific values ​​of the second proportional coefficient and the second integral coefficient can be adjusted as needed, and are not specifically limited here. In at least one embodiment of the present application, a comparison table of the saturated evaporation temperature and pressure of at least one refrigerant is usually stored in the vehicle 100, and the target pressure value can be obtained by looking up the table according to the target refrigeration temperature. The target pressure value is related to the type of refrigerant in the first condensing component 20 and the target refrigeration temperature. In at least one embodiment of the present application, the refrigerant in the first condensing component 20 can be R134a, but it is not limited thereto.

[0055] One end of the HVAC component 40 is connected to the first condensing component 20 through the first pipeline 101, and the other end is connected to the second condensing component 50 through the second pipeline 102. The HVAC component 40 is used to evaporate the low-pressure liquid and simultaneously provide gas and liquid to the second condensing component 50. In at least one embodiment of the present application, the HVAC component 40 is a heating, ventilation and air conditioning (HVAC) component.

[0056] The second condensing assembly 50 is used to absorb heat from the air outside the vehicle 100 to perform secondary evaporation on the gas and provide the secondary evaporated gas to the compressor 10. In at least one embodiment of the present application, the second condensing assembly 50 includes an outdoor heat exchanger (OHX).

[0057] The second electronic expansion valve 60 is disposed on the second pipeline 102. The second electronic expansion valve 60 is used to decompress the gas in the second pipeline 102 to form a low-pressure liquid and provide it to the second condensing assembly 50. The opening of the second electronic expansion valve 60 can be set according to the second real-time pressure and the second real-time temperature in the third pipeline 103 and the target superheat. In at least one embodiment of the present application, the opening of the second electronic expansion valve 60 can be calculated based on the timing superheat of the gas entering the compressor 10 and the target superheat. Specifically, the actual superheat can be calculated by the following formula three.

[0058] Formula 3 in, is the actual superheat of the compressor 10, is the second real-time temperature, It is a pressure-saturation temperature function corresponding to the refrigerant type in the first condensing component 20.

[0059] The opening degree of the second electronic expansion valve 60 can be calculated by the following formula 4.

[0060] Formula 4 in, is the opening percentage of the second electronic expansion valve 60, is the third proportionality coefficient, is the actual superheat of the compressor 10, is the third integral coefficient, is the target superheat. In at least one embodiment of the present application, the third proportional coefficient is 0.1 and the third integral coefficient is 0.05, but it is not limited thereto. In other embodiments, the specific values ​​of the second proportional coefficient and the third integral coefficient can be adjusted according to the needs, and are not specifically limited here.

[0061] The first sensor 70 is disposed on the first pipeline 101 and is close to the air inlet of the HVAC component 40. The first sensor 70 is used to sense the first real-time pressure in the first pipeline 101.

[0062] The second sensor 80 is disposed on the third pipeline 103 and is close to the air outlet of the HVAC component 40. The second sensor 80 is used to sense the second real-time pressure and the second real-time temperature in the third pipeline 103. In at least one embodiment of the present application, the second sensor 80 is a pressure and temperature sensor.

[0063] See also Figure 4 , which is a block diagram of a vehicle 100 of at least one embodiment of the present application. The vehicle 100 is a hybrid vehicle. It is understood that the present application does not limit the type of the vehicle 100, for example, it can be a plug-in hybrid vehicle or a gasoline-electric hybrid vehicle. Among them, the vehicle 100 uses a fuel cell as a power source.

[0064] The vehicle 100 includes a thermal management control system 1, a battery heating control system 2, an air conditioning control system 3, a processor 4, a memory 5, and a communication interface 6. The thermal management control system 1, the battery heating control system 2, the air conditioning control system 3, the processor 4, the memory 5, and the communication interface 6 can be connected through a communication bus and communicate with each other.

[0065] The specific content of the thermal management control system 1 can refer to the specific description of the thermal management control method mentioned above, which will not be described in detail here.

[0066] The processor 4 may be a general purpose central processing unit (CPU), a microprocessor, an application-specific integrated circuit (ASIC), or one or more integrated circuits for controlling the execution of the above program.

[0067] The memory 5 may be a read-only memory (ROM) or other types of static storage devices that can store static information and instructions, a random access memory (RAM) or other types of dynamic storage devices that can store information and instructions, or an electrically erasable programmable read-only memory (EEPROM), a compact disc read-only memory (CD-ROM) or other optical disc storage, optical disc storage (including compressed optical disc, laser disc, optical disc, digital versatile disc, Blu-ray disc, etc.), a magnetic disk storage medium or other magnetic storage device, or any other medium that can be used to carry or store the desired program code in the form of instructions or data structures and can be accessed by a computer, but is not limited thereto. The memory 5 may exist independently and be connected to the processor 4 via a bus. The memory 5 may also be integrated with the processor 4.

[0068] The memory 5 is used to store program instructions for executing the above scheme, and the execution is controlled by the processor 4. The processor 4 is used to execute the program instructions stored in the memory 5. The program instructions stored in the memory 5 can be executed Figure 1 as well as Figure 2 Part or all of the steps of the thermal management control method described in.

[0069] The communication interface 6 is used to communicate with other devices or communication networks, such as Ethernet, Radio Access Network (RAN), Wireless Local Area Networks (WLAN), etc.

[0070] The embodiment of the present application also provides a computer-readable storage medium. The computer-readable storage medium stores program instructions, and when the program instructions are executed on a computing device, the computing device executes the thermal management control method provided by the above embodiment.

[0071] It is obvious to those skilled in the art that the present application is not limited to the details of the above exemplary embodiments, and that the present application can be implemented in other specific forms without departing from the spirit or basic features of the present application. Therefore, as long as they are within the scope of the essence and spirit of the present application, appropriate changes and modifications made to the above embodiments should fall within the scope of protection claimed in the present application.

Claims

1. A thermal management control method, characterized in that: The thermal management control method comprises: A target heating temperature is calculated based on a heat source demand in the vehicle, and a target cooling temperature is calculated based on a cooling demand in the vehicle; wherein the target heating temperature is greater than the target cooling temperature; The speed of the compressor is set according to the target heating temperature and the first real-time temperature in the first pipeline; wherein the first pipeline connects the first condensing component and the HVAC component; setting the opening of the first electronic expansion valve according to the target refrigeration temperature and the first real-time pressure in the first pipeline; Using the HVAC component to evaporate the liquid and generate gas, using a second pipeline to provide the gas to a second condensation component, and using the second condensation component to evaporate the gas for a second time; and The opening degree of the second electronic expansion valve is set according to the second real-time pressure and the second real-time temperature in the third pipeline between the second condensing component and the compressor and the target superheat degree.

2. The thermal management control method according to claim 1, characterized in that The step of setting the opening of the second electronic expansion valve according to the second real-time pressure and the second real-time temperature in the third pipeline and the target superheat further comprises: calculating the actual superheat of the gas entering the compressor according to the second real-time pressure in the third pipeline and the second real-time temperature; and The opening degree of the second electronic expansion valve is set according to the actual superheat degree and the target superheat degree.

3. The thermal management control method according to claim 1, characterized in that: The speed of the compressor is calculated according to the following formula: ,in, is the speed of the compressor, is the first proportionality coefficient, is the first integral coefficient; The difference between the target heating temperature and the first real-time temperature is the first real-time temperature.

4. The thermal management control method according to claim 1, characterized in that: The opening degree of the first electronic expansion valve is calculated using the following formula: ,in, is the opening degree of the first electronic expansion valve, is the second proportionality coefficient, Δ2 is the difference between the target pressure and the first real-time pressure, is the second integral coefficient.

5. The thermal management control method according to claim 2, characterized in that: The actual superheat is calculated according to the following formula: ,in, is the actual superheat, is the second real-time temperature in the third pipeline, is the pressure-saturation temperature function corresponding to the first condensation component.

6. The thermal management control method according to claim 2, characterized in that: The opening degree of the second electronic expansion valve is calculated using the following formula: ,in, is the opening percentage of the second electronic expansion valve, is the third proportionality coefficient, is the actual superheat, is the third integral coefficient, is the target superheat.

7. The thermal management control method according to claim 1, characterized in that: The first electronic expansion valve is arranged on the first pipeline and is close to the HVAC component; the third pipeline connects the second condensing component and the compressor, and the second electronic expansion valve is arranged on the third pipeline and is close to the compressor.

8. A thermal management control system, characterized in that: The thermal management control system comprises: A compressor, configured to set a speed of the compressor according to a target heating temperature calculated based on a heat source demand in the vehicle and a first real-time temperature in a first pipeline; wherein the first pipeline connects a first condensing component and a HVAC component; a first electronic expansion valve, configured to set its corresponding opening degree according to a target cooling temperature calculated according to a cooling demand in the vehicle and a first real-time pressure in the first pipeline; wherein the target heating temperature is greater than the target cooling temperature; HVAC components for evaporating liquids to form gases; A second condensing component, used for receiving the gas provided by the HVAC component through a second pipeline and performing secondary evaporation; The second electronic expansion valve is used to set its corresponding opening degree according to the second real-time pressure and the second real-time temperature in the third pipeline between the second condensing component and the compressor and the target superheat.

9. The thermal management control system according to claim 8, characterized in that: The thermal management control system also includes a first sensor and a second sensor; the first sensor is arranged on the first pipeline and is close to the HVAC component; the first sensor is used to sense a first real-time pressure in the first pipeline; the second sensor is arranged on the third pipeline and is close to the compressor; the second sensor is used to sense a second real-time pressure and a second real-time temperature in the third pipeline.

10. A vehicle, characterized in that: The vehicle includes a processor and a memory, the memory is used to store a plurality of program instructions, and when the processor calls the program instructions, the thermal management control method as described in any one of claims 1 to 7 is implemented.

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