Vehicle-mounted heat management system with working medium volatility matching

Abstract

The application discloses a working medium volatility matched vehicle-mounted heat management system, which comprises an engine, a waste heat recovery subsystem, a refrigeration subsystem and a liquid separation condenser. The vehicle-mounted heat management system adopts a non-azeotropic mixed working medium as the working medium. On the basis of realizing collaborative heat management of a low-temperature waste heat source, a high-temperature waste heat source, a low-temperature refrigeration object and a high-temperature refrigeration object, the original charging working medium is separated into high and low volatility working media by the liquid separation condenser. Based on the characteristic that the high volatility working medium has higher evaporation pressure than the original charging working medium at the same evaporation temperature, the evaporation pressure of the system is improved, and then the energy conversion efficiency of the system and the energy saving effect of the whole vehicle are improved.

Description

Technical Field

[0001] This invention relates to the field of vehicle energy-saving technology, and more specifically to an on-board thermal management system with matching working fluid volatility. Background Technology

[0002] Vehicle thermal management systems need to reduce various types of waste heat from the engine to temperatures conducive to engine operation and to cool the vehicle's power battery, cabin, refrigerator, and other components. Engine waste heat utilization technology based on the Rankine cycle can achieve waste heat temperature control and reduce engine fuel consumption, while refrigeration technology based on a dual-pressure vapor compression refrigeration cycle can achieve dual evaporation temperatures to match diverse cooling needs. The two cycles can share a condenser to form a combined cooling and electrical cycle, representing a novel vehicle thermal management system.

[0003] However, the engine generates multiple streams of waste heat, with temperature differences reaching hundreds of degrees Celsius, and the evaporation temperature requirements of multiple refrigeration objects also differ by tens of degrees. If the combined cooling and power cycle meets thermal management requirements, the circulating working fluid must be heated to at least a saturated gaseous state when flowing through the heat exchangers of the low-temperature waste heat source and the low-temperature refrigeration object. However, the evaporation pressure required for low-temperature evaporation is relatively low, resulting in a decrease in the expander's work capacity and an increase in compressor energy consumption, thus limiting the energy-saving effect of the vehicle's thermal management system. Summary of the Invention

[0004] In view of the above background and current technology, the main objective of this invention is to provide an on-board thermal management system with matching working fluid volatility, which can synergistically improve the evaporation pressure of the waste heat recovery subsystem and the refrigeration subsystem in the on-board thermal management system, thereby improving the performance of the expander and compressor and reducing vehicle energy consumption.

[0005] This invention provides an on-board thermal management system with matched working fluid volatility, including an engine, a waste heat recovery subsystem, a refrigeration subsystem, and a liquid separator condenser;

[0006] The engine provides a low-temperature waste heat source and a high-temperature waste heat source to the waste heat recovery subsystem;

[0007] The waste heat recovery subsystem includes a low-volatility working fluid pump, a high-volatility working fluid pump, a low-volatility working fluid heater, a high-volatility working fluid heater, a medium-volatility working fluid heater, and an expander. The outlet of the low-volatility working fluid pump is connected to the working fluid-side inlet of the low-volatility working fluid heater. The outlet of the high-volatility working fluid pump is connected to the working fluid-side inlet of the high-volatility working fluid heater. The working fluid-side inlet of the medium-volatility working fluid heater is connected to the confluence point of the low-temperature working fluid-side outlet of the low-volatility working fluid heater and the working fluid-side outlet of the high-volatility working fluid heater. The working fluid-side outlet of the medium-volatility working fluid heater is connected to the inlet of the expander. The outlet of the expander is connected to the high-temperature working fluid-side inlet of the low-volatility working fluid heater. The low-temperature waste heat source flows through the heat source side of the medium-volatility working fluid heater, and the high-temperature waste heat source flows through the heat source side of the low-volatility working fluid heater.

[0008] The refrigeration subsystem includes a low-volatility refrigerant throttling valve, a high-volatility refrigerant throttling valve, a low-volatility refrigerant evaporator, a high-volatility refrigerant evaporator, a low-volatility refrigerant pressure reducing valve, and a compressor. The outlet of the low-volatility refrigerant throttling valve is connected to the inlet on the refrigerant side of the low-volatility refrigerant evaporator. The outlet on the refrigerant side of the high-volatility refrigerant evaporator is connected to the inlet on the low-volatility refrigerant pressure reducing valve. The inlet of the compressor is connected to the intersection of the outlet on the refrigerant side of the high-volatility refrigerant evaporator and the outlet of the low-volatility refrigerant pressure reducing valve.

[0009] The inlet of the working fluid side of the liquid separator is connected to the intersection of the outlet of the compressor and the outlet of the high-temperature working fluid side of the low-volatility working fluid heater. The first outlet of the working fluid side of the liquid separator is connected to the inlet of the low-volatility working fluid pump and the inlet of the low-volatility working fluid throttling valve. The second outlet of the working fluid side of the liquid separator is connected to the inlet of the high-volatility working fluid pump and the inlet of the high-volatility working fluid throttling valve.

[0010] Non-azeotropic working fluids are circulated in the waste heat recovery subsystem, the refrigeration subsystem, and the liquid separator condenser.

[0011] The volatility of the non-azeotropic working fluid flowing through the working fluid side of the low-volatility working fluid pump, the low-volatility working fluid heater, the low-volatility working fluid throttling valve, the low-temperature working fluid side of the low-volatility working fluid evaporator, the low-volatility working fluid pressure reducing valve, and the first outlet of the working fluid side of the separatory condenser is defined as Class I. The volatility of the non-azeotropic working fluid flowing through the first flow of the expander, the compressor, the high-temperature working fluid side of the low-volatility working fluid heater (4), and the working fluid side of the separatory condenser is defined as Class II. The volatility of the non-azeotropic working fluid flowing through the working fluid side of the high-volatility working fluid pump, the high-volatility working fluid heater, the high-volatility working fluid throttling valve, the working fluid side of the high-volatility working fluid evaporator, the second flow of the working fluid side of the separatory condenser, and the second outlet of the working fluid side of the separatory condenser is defined as Class III.

[0012] The volatility of Level I, Level II, and Level III increases sequentially.

[0013] According to an embodiment of the present invention, the type of low-temperature waste heat source includes either cold air from the engine or engine coolant;

[0014] According to an embodiment of the present invention, the high-temperature waste heat source includes either engine exhaust or engine recirculated exhaust gas.

[0015] According to an embodiment of the present invention, the low-volatility working fluid evaporator and the high-volatility working fluid evaporator can respectively provide cooling energy to the power battery and the cabin, or respectively to the power battery and the refrigerator, or respectively to the cabin and the refrigerator; the required evaporation temperatures of the power battery, the cabin, and the refrigerator decrease sequentially.

[0016] As can be seen from the above technical solution, the vehicle thermal management system with matched working fluid volatility provided by the present invention has the following beneficial effects:

[0017] (1) Highly volatile working fluid is used to recover low-temperature waste heat, which can effectively increase the evaporation pressure of the waste heat recovery subsystem, thereby increasing the expander pressure ratio, which is conducive to the waste heat recovery subsystem outputting more net power and can effectively reduce engine fuel consumption.

[0018] (2) Highly volatile working fluids are used to provide cooling to low-temperature refrigeration objects, which can effectively increase the evaporation pressure of the refrigeration subsystem, thereby reducing the compressor pressure ratio. This is beneficial for the compressor in the refrigeration subsystem to consume less electrical energy, which can effectively reduce the vehicle's power consumption.

[0019] (3) It has a wide range of applications and can be applied to vehicles where the engine is one of the prime movers and two evaporation temperature requirements are required, such as hybrid electric vehicles (where the engine is one of the prime movers and the cabin and power battery require two evaporation temperatures), fuel cold chain logistics vehicles (where the engine is the prime mover and the cabin and freezer require two evaporation temperatures), and hybrid cold chain logistics vehicles (where the engine is one of the prime movers and the power battery and freezer require two evaporation temperatures). Attached Figure Description

[0020] Figure 1 This invention relates to the structure and schematic diagram of an on-board thermal management system with matching working fluid volatility.

[0021] In the picture:

[0022] 1-Engine, 2-Low-volatile working fluid pump, 3-High-volatile working fluid pump, 4-Low-volatile working fluid heater, 5-High-volatile working fluid heater, 6-Medium-volatile working fluid heater, 7-Expander, 8-Low-volatile working fluid throttle valve, 9-High-volatile working fluid throttle valve, 10-Low-volatile working fluid evaporator, 11-High-volatile working fluid evaporator, 12-Low-volatile working fluid pressure reducing valve, 13-Compressor, 14-Separate liquid condenser, E1-First outlet on the working fluid side of the separate liquid condenser, E2-Second outlet on the working fluid side of the separate liquid condenser, F1-First flow path on the working fluid side of the separate liquid condenser, F2-Second flow path on the working fluid side of the separate liquid condenser; a-First flow channel of high-temperature waste heat source; b-Second flow channel of high-temperature waste heat source. Detailed Implementation

[0023] The technical solution of the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. The specific embodiments described are only for explanation and illustration of the present invention and are not intended to limit the present invention.

[0024] like Figure 1 As shown, the present invention provides an on-board thermal management system with matching working fluid volatility. The system structure specifically comprises an engine 1, a waste heat recovery subsystem, a refrigeration subsystem, and a liquid separator condenser 14.

[0025] The engine 1 provides a low-temperature waste heat source and a high-temperature waste heat source to the waste heat recovery subsystem. The low-temperature waste heat source outlet of the engine 1 is connected to the hot fluid side inlet of the high-volatility working fluid heater 5, the low-temperature waste heat source inlet of the engine 1 is connected to the hot fluid side outlet of the high-volatility working fluid heater 5, and the high-temperature waste heat source outlet of the engine 1 is connected to the hot fluid side inlet of the medium-volatility heater 6.

[0026] The waste heat recovery subsystem includes a low-volatility working fluid pump 2, a high-volatility working fluid pump 3, a low-volatility working fluid heater 4, a high-volatility working fluid heater 5, a medium-volatility working fluid heater 6, and an expander 7. The outlet of the low-volatility working fluid pump 2 is connected to the low-temperature working fluid side inlet of the low-volatility working fluid heater 4; the outlet of the high-volatility working fluid pump 3 is connected to the working fluid side inlet of the high-volatility working fluid heater 5; and the working fluid side inlet of the medium-volatility working fluid heater 6 is connected to the... The outlet of the low-volatility working fluid heater 4 on the low-temperature working fluid side and the outlet of the high-volatility working fluid heater 5 on the working fluid side are connected at the confluence point. The outlet of the medium-volatility working fluid heater 6 on the working fluid side is connected to the inlet of the expander 7. The outlet of the expander 7 is connected to the inlet of the low-volatility working fluid heater 4 on the high-temperature working fluid side. The low-temperature waste heat source flows through the heat source side of the high-volatility working fluid heater 5, and the high-temperature waste heat source flows through the heat source side of the medium-volatility working fluid heater 6.

[0027] The refrigeration subsystem includes a low-volatility refrigerant throttling valve 8, a high-volatility refrigerant throttling valve 9, a low-volatility refrigerant evaporator 10, a high-volatility refrigerant evaporator 11, a low-volatility refrigerant pressure reducing valve 12, and a compressor 13. The outlet of the low-volatility refrigerant throttling valve 8 is connected to the inlet on the refrigerant side of the low-volatility refrigerant evaporator 10; the outlet of the high-volatility refrigerant throttling valve 9 is connected to the inlet on the refrigerant side of the high-volatility refrigerant evaporator 11; the outlet on the refrigerant side of the high-volatility refrigerant evaporator 11 is connected to the inlet of the low-volatility refrigerant pressure reducing valve 12; and the inlet of the compressor 13 is connected to the intersection of the outlet on the refrigerant side of the high-volatility refrigerant evaporator 11 and the outlet of the low-volatility refrigerant pressure reducing valve 12.

[0028] The inlet of the working fluid side of the liquid separator condenser 14 is connected to the intersection of the outlet of the compressor 13 and the outlet of the high-temperature working fluid side of the low-volatility working fluid heater 4. The first outlet E1 on the working fluid side of the liquid separator condenser is split into two paths: one path is connected to the inlet of the low-volatility working fluid pump 2, and the other path is connected to the inlet of the low-volatility working fluid throttling valve 8. The second outlet E2 on the working fluid side of the liquid separator condenser is split into two paths: one path is connected to the inlet of the high-volatility working fluid pump 3, and the other path is connected to the inlet of the high-volatility working fluid throttling valve 9.

[0029] Non-azeotropic working fluids are circulated in the waste heat recovery subsystem, the refrigeration subsystem, and the liquid separator condenser.

[0030] The volatility of the non-azeotropic working fluid flowing through the low-volatility working fluid pump 2, the low-volatility working fluid heater 4 (low-temperature working fluid side), the low-volatility working fluid throttling valve 8, the working fluid side of the low-volatility working fluid evaporator 10, the low-volatility working fluid pressure reducing valve 12, and the first outlet E1 of the working fluid side of the separatory condenser is defined as Class I. The volatility of the non-azeotropic working fluid flowing through the expander 7, the compressor 13, the high-temperature working fluid side of the low-volatility working fluid heater 4, and the first flow F1 of the working fluid side of the separatory condenser is defined as Class II. The volatility of the non-azeotropic working fluid flowing through the high-volatility working fluid pump 3, the high-volatility working fluid heater 5 (working fluid side), the high-volatility working fluid throttling valve 9, the high-volatility working fluid evaporator 11 (working fluid side), the second flow F2 of the working fluid side of the separatory condenser, and the second outlet E2 of the working fluid side of the separatory condenser is defined as Class III.

[0031] The volatility of Level I, Level II, and Level III increases sequentially.

[0032] The types of low-temperature waste heat sources include either cold air from the engine or engine coolant.

[0033] The types of high-temperature waste heat sources include engine exhaust and engine recirculated exhaust gas.

[0034] If the high-temperature waste heat source is engine recirculation exhaust gas, then the high-temperature waste heat source inlet of the engine 1 is connected to the hot fluid side outlet of the medium volatile heater 6, and the high-temperature waste heat source flows in the first flow channel a of the high-temperature waste heat source; if the high-temperature waste heat source is engine exhaust, then the engine 1 has no high-temperature waste heat source inlet, and the high-temperature waste heat source flows in the second flow channel b of the high-temperature waste heat source until it is discharged outside the vehicle.

[0035] The low-volatility working fluid evaporator 10 and the high-volatility working fluid evaporator 11 can respectively provide cooling energy to the power battery and the cabin, or respectively provide cooling energy to the power battery and the refrigerator, or respectively provide cooling energy to the cabin and the refrigerator.

[0036] The required evaporation temperatures of the power battery, the cabin, and the refrigerator decrease sequentially.

[0037] The non-azeotropic working medium includes, but is not limited to, a mixture of trans-1-chloro-3,3,3-trifluoropropene and 1,3,3,3-tetrafluoropropene, a mixture of trans-1-chloro-3,3,3-trifluoropropene and propane, and a mixture of trans-1-chloro-3,3,3-trifluoropropene and difluoromethane.

[0038] After the volatile working fluid flows into the gas-liquid separator 14, the first flow F1, which flows through the working fluid side of the liquid separator condenser, is cooled into a two-phase state.

[0039] For the working fluid in the first process F1, which is in a two-phase state and flows out of the working fluid side of the liquid-liquid condenser, the liquid low-volatility working fluid flows out from the first outlet E1 of the working fluid side of the liquid-liquid condenser, while the gaseous high-volatility working fluid flows into the second process F2 of the working fluid side of the liquid-liquid condenser and is cooled into a subcooled liquid or saturated liquid, and flows out from the second outlet E2 of the working fluid side of the liquid-liquid condenser; the outflowing high and low volatile working fluids are split, with part flowing into the waste heat recovery subsystem and the other part flowing into the refrigeration subsystem;

[0040] The low-volatility working fluid flowing into the waste heat recovery subsystem is pressurized by the low-volatility working fluid pump 2 and flows into the low-volatility working fluid heater 4 at the low temperature. The high-volatility working fluid flowing into the waste heat recovery subsystem is pressurized by the high-volatility working fluid pump 3 and flows into the high-volatility working fluid heater 5 at the working fluid side, where it is heated to a saturated gaseous state or a superheated state by the low-temperature waste heat source flowing out of the engine 1. The high- and low-volatility working fluids that flow out are mixed and become a medium-volatility working fluid, which flows into the medium-volatility working fluid heater 6 at the working fluid side, where it is heated to a superheated state by the high-temperature waste heat source flowing out of the engine 1. The superheated medium-volatility working fluid flows into the expander 7 to do work, and then flows into the high-temperature working fluid side of the low-volatility working fluid heater 4 to release heat.

[0041] The low-volatility refrigerant flowing into the refrigeration subsystem is throttled to a two-phase state by the low-volatility refrigerant throttling valve 8, and then flows into the low-volatility refrigerant evaporator 10 to output higher-temperature cooling energy. The low-volatility refrigerant flowing out is throttled to the same pressure as the high-volatility refrigerant evaporator 11 by the low-volatility refrigerant pressure reducing valve 12. The high-volatility refrigerant flowing into the refrigeration subsystem is throttled to a two-phase state by the high-volatility refrigerant throttling valve 9, and then flows into the high-volatility refrigerant evaporator 11 to output lower-temperature cooling energy. The high and low-volatility refrigerants flowing out are mixed and become a medium-volatility refrigerant, which is then pressurized by the compressor 13.

[0042] The high-temperature working fluid from the low-volatility working fluid heater 4 and the medium-volatility working fluid from the compressor 13 merge and flow into the liquid separator condenser 14, completing one cycle;

[0043] The low-temperature waste heat source flowing out of the engine 1 releases heat in the high-volatility working fluid heater 5 and then returns to the engine 1; depending on the type of high-temperature waste heat source, the high-temperature waste heat source flowing out of the engine 1 releases heat in the medium-volatility working fluid heater 6 and then returns to the engine 1 via the first flow channel a of the high-temperature waste heat source (the high-temperature waste heat source is engine recirculated exhaust gas) or is directly discharged outside the vehicle via the second flow channel b of the high-temperature waste heat source (the high-temperature waste heat source is engine exhaust gas).

[0044] Example:

[0045] The working fluid side of the liquid-liquid separator 14 has two flows: a first flow F1 and a second flow F2. The moderately volatile working fluid enters the first flow F1 and is gradually condensed into a two-phase state. According to the principle of gas-liquid phase equilibrium, the volatility of the liquid working fluid in the two-phase state is lower than that of the moderately volatile working fluid, and the volatility of the gaseous working fluid is higher than that of the moderately volatile working fluid. When the moderately volatile working fluid flows through the first flow F1 of the liquid-liquid separator, the liquid working fluid flows out from the first outlet E1 of the liquid-liquid separator, becoming a low-volatility working fluid. Then, the highly volatile working fluid is further cooled into a liquid state in the second flow F2 of the liquid-liquid separator and flows out from the second outlet E2 of the liquid-liquid separator, becoming a highly volatile working fluid.

[0046] Within the waste heat recovery subsystem, a highly volatile working fluid flows into the working fluid side of the highly volatile working fluid heater 5 to absorb heat from the low-temperature waste heat source, reducing its temperature to a specified temperature or a specified temperature range. Compared to a medium-volatile working fluid, the highly volatile working fluid can be heated to a saturated gaseous state or a superheated state at a higher evaporation pressure, thus increasing the inlet pressure of the expander 7. This is beneficial for the expander 7 to perform work and improve engine thermal efficiency, thereby reducing engine fuel consumption. A low-volatile working fluid flows into the low-temperature working fluid side of the low-volatile working fluid heater 4 to absorb heat from the exhaust gas of the expander 7. The highly and low-volatile working fluids combine to form a medium-volatile working fluid, which flows into the medium-volatile working fluid heater 6 to absorb heat from the high-temperature waste heat source, reducing its temperature to a specified temperature or a specified temperature range before flowing into the expander 7 to perform work. It then flows into the high-temperature working fluid side of the low-volatile working fluid heater 4 to release heat.

[0047] Within the refrigeration subsystem, the highly volatile refrigerant flows into the highly volatile refrigerant throttling valve 9 and is throttled to a two-phase state. This refrigerant is then used in the highly volatile refrigerant evaporator 11 to absorb heat from the low-temperature refrigerated object, lowering its temperature to a specified temperature or a specified temperature range. Compared to the medium-volatile refrigerant, the highly volatile refrigerant can be heated to a saturated gaseous state or a superheated state at a higher evaporation pressure, thus increasing the inlet pressure of the compressor 13 and reducing the power consumption of the compressor 13 and the vehicle's overall power consumption. The low-volatile refrigerant flows into the low-volatile refrigerant evaporator 10 to absorb heat from the high-temperature refrigerated object, lowering its temperature to a specified temperature or a specified temperature range. The outflowing low-volatile refrigerant is pressure-reduced by the low-volatile refrigerant pressure reducing valve 12 to the same pressure as the outflowing highly volatile refrigerant. The high and low volatile refrigerants combine to form the medium-volatile refrigerant, which flows into the compressor 13 and is pressurized.

[0048] The medium-volatile working fluid flowing out of the high-temperature working fluid side of the low-volatile working fluid heater 4 merges with the medium-volatile working fluid flowing out of the compressor 13 and flows into the liquid separator condenser 14, where the staged condensation process is completed in two flows.

[0049] Boundary conditions: In the waste heat recovery subsystem of this embodiment, the high-temperature waste heat source is engine exhaust, and the low-temperature waste heat source is engine coolant; in the refrigeration subsystem, the low-volatility working fluid evaporator and the high-volatility working fluid evaporator provide cooling energy to the power battery and the cabin, respectively; the parameters of the above boundary conditions are shown in the table below.

[0050]

[0051] System working fluid: a mixture of trans-1-chloro-3,3,3-trifluoropropene and 1,3,3,3-tetrafluoropropene in a mass fraction ratio of 35%:65%, and this mass fraction mixture is defined as a medium volatile working fluid;

[0052] Implementation results:

[0053] (1) Control group (working fluid volatility mismatch): The liquid separator condenser 14 is replaced with a conventional condenser (wherein, the difference between the conventional condenser and the liquid separator condenser in this embodiment is only that: the conventional condenser only has the first flow path F1 on the working fluid side of the liquid separator condenser and the first outlet E1 on the working fluid side of the liquid separator condenser. After passing through the first flow path F1 in the conventional condenser, the working fluid is cooled to a saturated liquid or subcooled state and flows out from the first outlet E1, and is transported to the waste heat recovery subsystem and the refrigeration subsystem). All working fluids in the system are medium volatile working fluids;

[0054] (2) Implementation effect: The inlet pressure of the expander in this embodiment is 7.51% higher than that of the control group, which makes the output power of the expander 7.46% higher than that of the control group; the inlet pressure of the compressor in this embodiment is 13.51% higher than that of the control group, which makes the power consumption of the compressor 8.76% lower than that of the control group; the implementation effect shows that the present invention can reduce engine oil consumption and vehicle power consumption, and has a superior overall vehicle energy saving effect.

[0055] parameter unit Effect of this embodiment Effects of mismatched working fluid volatility Relative increase (%) Expander inlet pressure MPa 1.546 1.438 7.51 Compressor inlet pressure MPa 0.126 0.111 13.51 Expander output power kW 3.445 3.702 7.46 Compressor power consumption kW 1.826 1.679 8.76

[0056] The parts of this invention not described in detail are well-known to those skilled in the art. The embodiments described above are merely preferred embodiments of the invention, and do not exhaustively describe all details, nor do they limit the invention to the specific implementations described. Various modifications and improvements to the technical solutions of this invention made by those skilled in the art without departing from the spirit of the invention should fall within the protection scope defined by the claims of this invention.

Claims

1. An on-board thermal management system with matching working fluid volatility, comprising an engine (1), a waste heat recovery subsystem, a refrigeration subsystem, and a liquid separator condenser (14). The engine (1) provides a low-temperature waste heat source and a high-temperature waste heat source to the waste heat recovery subsystem; The waste heat recovery subsystem includes a low-volatility working fluid pump (2), a high-volatility working fluid pump (3), a low-volatility working fluid heater (4), a high-volatility working fluid heater (5), a medium-volatility working fluid heater (6), and an expander (7). The outlet of the low-volatility working fluid pump (2) is connected to the low-temperature working fluid side inlet of the low-volatility working fluid heater (4), the outlet of the high-volatility working fluid pump (3) is connected to the working fluid side inlet of the high-volatility working fluid heater (5), and the working fluid side inlet of the medium-volatility working fluid heater (6) is connected to the working fluid side inlet of the high-volatility working fluid heater (5). The outlet of the low-volatility working fluid heater (4) on the low-temperature working fluid side and the outlet of the high-volatility working fluid heater (5) on the working fluid side are connected to the junction point. The outlet of the medium-volatility working fluid heater (6) on the working fluid side is connected to the inlet of the expander (7). The outlet of the expander (7) is connected to the inlet of the low-volatility working fluid heater (4) on the high-temperature working fluid side. The low-temperature waste heat source flows through the heat source side of the high-volatility working fluid heater (5), and the high-temperature waste heat source flows through the heat source side of the medium-volatility working fluid heater (6). The refrigeration subsystem includes a low-volatility refrigerant throttling valve (8), a high-volatility refrigerant throttling valve (9), a low-volatility refrigerant evaporator (10), a high-volatility refrigerant evaporator (11), a low-volatility refrigerant pressure reducing valve (12), and a compressor (13). The outlet of the low-volatility refrigerant throttling valve (8) is connected to the inlet on the refrigerant side of the low-volatility refrigerant evaporator (10), the outlet of the high-volatility refrigerant throttling valve (9) is connected to the inlet on the refrigerant side of the high-volatility refrigerant evaporator (11), the outlet on the refrigerant side of the high-volatility refrigerant evaporator (11) is connected to the inlet of the low-volatility refrigerant pressure reducing valve (12), and the inlet of the compressor (13) is connected to the intersection of the outlet on the refrigerant side of the high-volatility refrigerant evaporator (11) and the outlet of the low-volatility refrigerant pressure reducing valve (12). The inlet of the working fluid side of the liquid separator (14) is connected to the intersection of the outlet of the compressor (13) and the outlet of the high-temperature working fluid side of the low-volatility working fluid heater (4). The first outlet (E1) of the working fluid side of the liquid separator is connected to the inlet of the low-volatility working fluid pump (2) and the inlet of the low-volatility working fluid throttling valve (8). The second outlet (E2) of the working fluid side of the liquid separator is connected to the inlet of the high-volatility working fluid pump (3) and the inlet of the high-volatility working fluid throttling valve (9). Non-azeotropic organic mixed working fluids circulate in the waste heat recovery subsystem, the refrigeration subsystem, and the liquid separator (14).

2. The system according to claim 1, wherein, The low-volatility working fluid pump (2), the low-volatility working fluid heater (4) at its low-temperature working fluid side, the low-volatility working fluid throttling valve (8), the working fluid side of the low-volatility working fluid evaporator (10), the low-volatility working fluid pressure reducing valve (12), and the non-azeotropic organic mixture flowing in the first outlet (E1) of the working fluid side of the separatory condenser are defined as having a volatility of Class I. The expander (7), the compressor (13), the low-volatility working fluid heater (4), and the... The volatility of the non-azeotropic organic mixture in the first flow (F1) of the working fluid side of the liquid separator is defined as Class II. The volatility of the non-azeotropic organic mixture flowing in the working fluid side of the high-volatility working fluid pump (3), the working fluid side of the high-volatility working fluid heater (5), the high-volatility working fluid throttling valve (9), the working fluid side of the high-volatility working fluid evaporator (11), the second flow (F2) of the working fluid side of the liquid separator, and the second outlet (E2) of the working fluid side of the liquid separator is defined as Class III. The volatility increases sequentially from Level I to Level II to Level III.

3. The system according to claim 1, wherein, The types of low-temperature waste heat sources include either the cold air in the engine or the engine coolant.

4. The system according to claim 1, wherein, The types of high-temperature waste heat sources include engine exhaust and engine recirculated exhaust gas.

5. The system according to claim 1, wherein, The low-volatility working fluid evaporator (10) and the high-volatility working fluid evaporator (11) respectively provide cooling energy to the power battery and the cabin, or respectively provide cooling energy to the power battery and the refrigerator, or respectively provide cooling energy to the cabin and the refrigerator; The required evaporation temperatures of the power battery, the cabin, and the refrigerator decrease sequentially.

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