Thermal management system and vehicle with same

Abstract

The invention discloses a heat management system and a vehicle with the same, the heat management system comprises a compression heat pump system and an absorption heat pump system, the compression heat pump system comprises a compressor and a first heat exchange branch, the first heat exchange branch is used for cabin and / or battery refrigeration, an air suction port of the compressor is connected with a first end of the first heat exchange branch, and a second end of the first heat exchange branch is connected with a second end of the absorption heat pump system; the absorption heat pump system comprises a refrigerant flow path and a generator, the refrigerant flow path is connected with an exhaust port of the compressor and the second end of the first heat exchange branch, and a part of the refrigerant flow path is located in the generator so as to exchange heat with the liquid working medium. According to the heat management system, the temperature of the refrigerant entering the first heat exchange branch can be adjusted through the absorption type heat pump system, the refrigerating capacity of the heat management system can be improved while the energy consumption of the compression type heat pump system is reduced, and the working performance of the heat management system is guaranteed to a certain degree.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle thermal management, and in particular to a thermal management system and a vehicle having the same. Background Art

[0002] The booming development of the new energy industry has brought new opportunities and challenges to electric vehicles, while also placing higher demands on the vehicle's thermal management system.

[0003] Among them, the vehicle's thermal management system is mostly a heat pump system with an electric compression heat pump as the power source. It is a relatively energy-saving and efficient system. Under cooling conditions, the system can take away the heat from the passenger compartment and / or battery pack, thereby achieving a cooling effect on the passenger compartment and / or battery pack to improve the comfort of the vehicle, extend the service life of the battery pack, and ensure the safety of the battery pack to a certain extent.

[0004] However, the insufficient cooling process of the above-mentioned thermal management system will lead to two problems: unstable system operation and poor comfort in the system passenger compartment, reducing the feasibility of the above-mentioned system in high-temperature areas. Summary of the Invention

[0005] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a thermal management system with a strong cooling capacity, which solves the technical problem of insufficient cooling process in the thermal management system of the prior art.

[0006] The present invention also aims to provide a vehicle having the above thermal management system.

[0007] According to an embodiment of the present invention, the thermal management system includes: a compression heat pump system, which includes a compressor and a first heat exchange branch, the first heat exchange branch is used for cabin and / or battery cooling, and the air intake of the compressor is connected to the first end of the first heat exchange branch; an absorption heat pump system, which includes a refrigerant flow path and a generator, the refrigerant flow path is respectively connected to the exhaust port of the compressor and the second end of the first heat exchange branch, and a portion of the refrigerant flow path is located in the generator for heat exchange with the liquid working medium.

[0008] According to the thermal management system of an embodiment of the present invention, an absorption heat pump system is set up, and the absorption heat pump system is set up to include a refrigerant flow path, and the refrigerant flow path is set up to be connected to the exhaust port of the compressor and the second end of the first heat exchange branch respectively. In this way, when the refrigerant discharged through the exhaust port of the compressor enters the first heat exchange branch to exchange heat with the cabin and / or the battery, it can first flow through the refrigerant flow path. Because a part of the refrigerant flow path is located in the generator of the absorption heat pump system, the refrigerant flowing through the refrigerant flow path can exchange heat with the liquid working fluid in the absorption heat pump system, so as to achieve the purpose of using the liquid working fluid to lower the refrigerant temperature, thereby achieving the purpose of using the absorption heat pump system to regulate the temperature of the refrigerant entering the first heat exchange branch. In this way, while reducing the energy consumption of the compression heat pump system, the refrigeration capacity of the thermal management system can also be improved, and the working performance of the thermal management system can be guaranteed to a certain extent.

[0009] In some embodiments, the absorption heat pump system further includes a first evaporator, the inlet end of the first evaporator is connected to the generator, and a portion of the refrigerant flow path is located in the first evaporator for heat exchange with the liquid working medium.

[0010] In some embodiments, the refrigerant flow path is connected in series with a throttling element located between the generator and the first evaporator.

[0011] In some embodiments, the absorption heat pump system further includes a first condenser and an absorber, wherein the first condenser is arranged between the generator and the inlet end of the first evaporator, and the absorber is arranged between the generator and the outlet end of the first evaporator, and the liquid working medium circulates among the first condenser, the first condenser, the first evaporator and the absorber.

[0012] In some embodiments, the absorption heat pump system further includes a solution pump, which is disposed between the generator and the absorber, and is used to control the flow rate of the liquid working medium between the first condenser, the first condenser, the first evaporator and the absorber.

[0013] In some embodiments, a recovery branch is provided between the generator and the absorber, and the recovery branch is used to transport the concentrated solution of the liquid working medium in the generator to the absorber.

[0014] In some embodiments, a first control valve is provided between the refrigerant flow path and the exhaust port of the compressor, and the first control valve is used to control the opening and closing of the refrigerant flow path and the exhaust port of the compressor.

[0015] In some embodiments, the first heat exchange branch includes a first branch, and the first branch is used for battery cooling.

[0016] In some embodiments, a heat exchanger and a second control valve are provided on the first branch. The heat exchanger is used for heat exchange with the battery. The second control valve is located between the heat exchanger and the refrigerant flow path. The second control valve is used to control the on and off of the first branch.

[0017] In some embodiments, the first heat exchange branch includes a second branch, and the second branch is used for cabin cooling.

[0018] In some embodiments, a second evaporator and a third control valve are provided on the second branch. The second evaporator is used for heat exchange with the cabin. The third control valve is located between the second evaporator and the refrigerant flow path. The third control valve is used to control the opening and closing of the second branch.

[0019] In some embodiments, the first heat exchange branch further includes a first branch, the first branch is used for battery cooling, and the first branch is connected in parallel with the second branch.

[0020] In some embodiments, the first end of the first branch is switchably connected to the intake port and the exhaust port, and the second end of the first branch is switchably connected to the refrigerant flow path and the intake port. When the first end of the first branch is connected to the intake port and the second end of the first branch is connected to the refrigerant flow path, it is used to cool the battery. When the first end of the first branch is connected to the exhaust port and the second end of the first branch is connected to the intake port, it is used to heat the battery.

[0021] In some embodiments, the compression heat pump system further has a second heat exchange branch for heating the cabin.

[0022] In some embodiments, the second heat exchange branch and the refrigerant flow path are connected in parallel.

[0023] In some embodiments, the thermal management system further includes a coolant system for dissipating heat from the electronic control module, and the coolant system exchanges heat with the compression heat pump system.

[0024] In some embodiments, the compression heat pump system includes a heat exchanger, which includes a first flow path and a second flow path for mutual heat exchange, the first flow path is connected between the second heat exchange branch and the suction port of the compressor, and the second flow path is part of the coolant system.

[0025] A vehicle according to an embodiment of the present invention includes the aforementioned thermal management system.

[0026] According to the vehicle of the embodiment of the present invention, by adopting the aforementioned thermal management system, the comfort of the vehicle's passenger compartment can be improved, the service life of the battery can be extended, and the safety of the battery can be guaranteed to a certain extent, thereby improving the driving experience.

[0027] Additional aspects and advantages of the invention will become apparent from the description which follows, or may be learned by practice of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments with reference to the following drawings, in which:

[0029] Figure 1 Schematic diagram of a thermal management system according to some embodiments of the present invention.

[0030] Figure 2 Schematic diagram of an absorption heat pump system according to some embodiments of the present invention.

[0031] Figure 3 This is a schematic diagram of a thermal management system according to some embodiments of the present invention operating in a first cooling mode.

[0032] Figure 4 This is a schematic diagram of a thermal management system according to some embodiments of the present invention operating in a second cooling mode.

[0033] Figure 5 This is a schematic diagram of a thermal management system according to some embodiments of the present invention operating in a third cooling mode.

[0034] Figure 6 This is a schematic diagram of a thermal management system according to some embodiments of the present invention operating in a first heating mode.

[0035] Figure 7 This is a schematic diagram of a thermal management system according to some embodiments of the present invention operating in a second heating mode.

[0036] Reference numerals:

[0037] 1000. Thermal management system;

[0038] 100. Compression heat pump system;

[0039] 110, compressor; 111, air intake; 112, air exhaust;

[0040] 120, first heat exchange branch;

[0041] 121, first branch; 1211, heat exchange element; 1212, second control valve;

[0042] 122, second branch; 1221, second evaporator; 1222, third control valve;

[0043] 130. First control valve;

[0044] 140. Second heat exchange branch; 141. Second condenser; 142. Eighth control valve;

[0045] 151. Fourth control valve; 152. Fifth control valve;

[0046] 153. Sixth control valve; 154. Seventh control valve;

[0047] 161. First one-way valve; 162. Second one-way valve;

[0048] 170. Gas-liquid separator;

[0049] 200. Absorption heat pump system;

[0050] 210. Refrigerant flow path; 211. Throttling element;

[0051] 220, generator; 230, first evaporator; 240, first condenser;

[0052] 250, absorber; 260, expansion valve; 270, solution pump; 280, recovery branch;

[0053] 300. Coolant system; 310. Heat exchanger. DETAILED DESCRIPTION

[0054] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0055] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0056] The thermal management system 1000 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0057] like Figure 1 As shown, a thermal management system 1000 according to an embodiment of the present invention includes: a compression heat pump system 100 and an absorption heat pump system 200 .

[0058] Among them, Figure 1 As shown, compression heat pump system 100 includes a compressor 110 and a first heat exchange branch 120. First heat exchange branch 120 is used for cabin and / or battery cooling. An air intake 111 of compressor 110 is connected to a first end of first heat exchange branch 120. This means that first heat exchange branch 120 is used for cabin cooling; or, first heat exchange branch 120 is used for battery cooling; or, first heat exchange branch 120 is used for both cabin and battery cooling. After first heat exchange branch 120 is used for cabin and / or battery cooling, refrigerant can be introduced into compressor 110 through air intake 111, thereby ensuring that the refrigerant can circulate and cool the cabin, thereby guaranteeing the performance of compression heat pump system 100 to a certain extent.

[0059] It should be noted that when the first heat exchange branch 120 is used for cabin cooling, it is mainly used to adjust the temperature in the cabin to ensure that the temperature in the cabin can be maintained within an appropriate range to a certain extent, thereby ensuring the comfort of vehicle use and improving the driving experience; when the first heat exchange branch 120 is used for battery cooling, it is mainly used to adjust the battery temperature to ensure that the battery temperature can be maintained within an appropriate range to a certain extent, thereby ensuring the battery's working performance and ensuring the safety of battery use.

[0060] It should also be noted that the battery mentioned here can be understood as a power source for the vehicle so that the vehicle can operate normally. In this way, when the thermal management system 1000 is applied to the vehicle, the first heat exchange branch 120 is used to adjust the battery temperature to ensure the battery's operating performance to a certain extent.

[0061] like Figure 1 As shown, the absorption heat pump system 200 includes a refrigerant flow path 210 and a generator 220. The refrigerant flow path 210 is connected to the exhaust port 112 of the compressor 110 and the second end of the first heat exchange branch 120 respectively. A portion of the refrigerant flow path 210 is located in the generator 220 to exchange heat with the liquid working medium. In other words, the compressor 110 of the compression heat pump system 100 has an intake port 111 and an exhaust port 112. The exhaust port 112 is connected to the refrigerant flow path 210 of the absorption heat pump system 200. The refrigerant flow path 210 is connected to the second end of the first heat exchange branch 120. The first end of the first heat exchange branch 120 is connected to the intake port 111 of the compressor 110. The exhaust port 112 is used to discharge the refrigerant in the compressor 110, and the intake port 111 is used to introduce the refrigerant into the compressor 110, so that the refrigerant can circulate between the compressor 110, the refrigerant flow path 210 and the first heat exchange branch 120.

[0062] Because a part of the refrigerant flow path 210 is located in the generator 220 and exchanges heat with the liquid working medium, when the refrigerant flows through the refrigerant flow path 210, heat exchange between the refrigerant and the liquid working medium can be realized. On the one hand, the purpose of using the liquid working medium to reduce the refrigerant temperature is achieved. On the other hand, the refrigerant in the refrigerant flow path 210 can also be used as the driving heat source of the absorption heat pump system 200 to drive the absorption heat pump system 200 to operate, eliminating the need to separately set up a driving heat source for the absorption heat pump system 200. While ensuring the working performance of the absorption heat pump system 200, the structure of the thermal management system 1000 can also be simplified.

[0063] In some embodiments, when the refrigerant flows through the refrigerant flow path 210 and exchanges heat with the liquid working fluid in the generator 220, in the generator 220, the liquid working fluid is used to reduce the temperature of the refrigerant, so that the liquid working fluid is heated by the high-temperature refrigerant. At this time, the absorbent in the liquid working fluid evaporates into vapor. In this process, the concentration of the liquid working fluid will also change to form a concentrated solution.

[0064] In a specific example, steam may escape from the generator 220 and enter the first condenser 240 , and the concentrated solution may be transported to the absorber 250 through the recovery branch 280 to ensure the working performance of the absorption heat pump system 200 , as will be described below.

[0065] It is worth noting that when the refrigerant exchanges heat with the liquid working medium, the refrigerant can be deeply cooled. The refrigerant with reduced temperature enters the first heat exchange branch 120 to achieve cooling of the cabin and / or battery, which to a certain extent ensures the working performance of the first heat exchange branch 120 and improves the cooling effect, while reducing the power consumption of the entire compression heat pump system 100.

[0066] Through the above configuration, the cooling effect of the compression heat pump system 100 can be effectively guaranteed, especially in high-temperature areas.

[0067] It is also worth noting that when the existing system cools the cabin and / or the battery, the refrigerant discharged through the exhaust port 112 of the compressor 110 is usually directly discharged into the external condenser in the form of convection heat exchange. This method not only causes heat waste, but also makes it impossible to reduce the temperature of the refrigerant in high-temperature areas, affecting the cooling effect of the cabin and / or the battery. In the present application, the refrigerant flow path 210 of the absorption heat pump system 200 is connected to the exhaust port 112 of the compressor 110, which actually recovers the existing refrigerant dissipated through the external condenser and introduces all the heat of the refrigerant dissipated through the external condenser into the absorption heat pump. System 200 drives the absorption heat pump system 200 to operate, which is a more complete and efficient way of waste heat recovery and utilization, making the energy utilization efficiency of the thermal management system 1000 higher, and achieving the purpose of deep cooling of the refrigerant by using the absorption heat pump system 200, thereby greatly improving the energy utilization rate, and reducing the primary energy consumption of the compression heat pump system 100 while ensuring the cooling capacity of the thermal management system 1000, thereby reducing the operating energy consumption of the thermal management system 1000, and can overcome a series of problems such as low efficiency of vehicle air conditioning and poor endurance of electric vehicles, that is, making the battery life of electric vehicles longer.

[0068] In summary, the thermal management system 1000 of the present application is coupled by a compression heat pump system 100 and an absorption heat pump system 200. The high-temperature and high-pressure refrigerant vapor passed into the external condenser for heat dissipation under the refrigeration condition of the compression heat pump system 100 is introduced into the generator 220 of the absorption heat pump system 200, driving the liquid working medium circulation inside the absorption heat pump system 200 to achieve refrigeration. In this system, the driving heat source quality of the absorption heat pump system 200 is higher, the greater the cooling capacity, the lower the overall system pressure, and the lower evaporation temperature can be achieved, providing more sufficient cooling capacity for the compression heat pump system 100.

[0069] As can be seen from the above structure, the thermal management system 1000 of the embodiment of the present invention is configured to include a compression heat pump system 100 and an absorption heat pump system 200 in order to improve the applicability of the thermal management system 1000 in high temperature areas, reduce the energy consumption of the compression heat pump system 100, obtain a lower evaporation temperature, and improve the refrigeration capacity of the compression heat pump system 100. The exhaust port 112 of the compressor 110 of the compression heat pump system 100 is configured to be connected to the refrigerant flow path 210 of the absorption heat pump system 200, and the refrigerant flow path 210 is connected to the first heat exchange branch 110 of the compression heat pump system 100. 20, and the first end of the first heat exchange branch 120 is connected to the air intake port 111 of the compressor 110, so that the refrigerant can circulate between the compressor 110, the refrigerant flow path 210 and the first heat exchange branch 120, thereby realizing heat exchange between the refrigerant and the liquid working fluid. In this way, not only a large amount of heat in the cabin is recovered as a driving heat source for the absorption heat pump system 200 to drive the absorption heat pump system 200 to operate, but the absorption heat pump system 200 can also be used to deeply cool the refrigerant, thereby improving the cooling effect of the thermal management system 1000 and enhancing the feasibility of the thermal management system 1000 in high temperature areas.

[0070] It can be understood that compared with the system in the prior art that achieves cooling at the expense of consuming battery power and sacrificing part of the cruising range, and at the same time directly discharges a large amount of high-quality heat carried by the refrigerant in the form of convection heat transfer in the condenser outside the vehicle, the present application adopts a suitable method to recover this part of the waste heat, which greatly improves the feasibility of the thermal management system 1000 in high temperature areas.

[0071] In some embodiments, combined Figure 1 and Figure 2 As shown, the absorption heat pump system 200 further includes a first evaporator 230. The inlet end of the first evaporator 230 is connected to the generator 220. A portion of the refrigerant flow path 210 is located within the first evaporator 230 to exchange heat with the liquid working medium. By connecting the inlet end of the first evaporator 230 to the generator 220, the circulation of the liquid working medium is facilitated, thereby ensuring the operating performance of the absorption heat pump system 200 to a certain extent.

[0072] In a specific example, after the liquid working medium enters the first evaporator 230, it absorbs heat from a low-temperature heat source (refrigerant referred to in this application) in the first evaporator 230, causing the liquid part of the liquid working medium to evaporate into a gaseous state. In this process, the temperature around the first evaporator 230 decreases, thereby achieving a cooling effect.

[0073] At this time, a portion of the refrigerant flow path 210 is located in the first evaporator 230 to exchange heat with the liquid working medium. The liquid working medium in the first evaporator 230 can be used to reduce the refrigerant temperature in the refrigerant flow path 210, so as to achieve deep cooling of the refrigerant in the refrigerant flow path 210, so that the refrigerant entering the first heat exchange branch 120 can effectively cool the cabin and / or battery, thereby improving the cooling effect.

[0074] In summary, the thermal management system 1000 of the present application not only exchanges heat between the refrigerant in the refrigerant flow path 210 and the liquid working medium in the generator 220, but also exchanges heat with the liquid working medium in the first evaporator 230 to achieve deep cooling of the refrigerant in the refrigerant flow path 210.

[0075] In a specific embodiment, combined with Figure 1 and Figure 2 As shown, one end of the refrigerant flow path 210 is connected to the exhaust port 112 of the compressor 110, and the other end of the refrigerant flow path 210 is connected to the first heat exchange branch 120. A portion of the refrigerant flow path 210 close to the exhaust port 112 of the compressor 110 is located in the generator 220 and exchanges heat with the liquid working medium in the generator 220. A portion of the refrigerant flow path 210 close to the first heat exchange branch 120 is located in the first evaporator 230 and exchanges heat with the liquid working medium in the first evaporator 230. In this way, when the refrigerant flows through the refrigerant flow path 210, it is first cooled in the generator 220 and then further deeply cooled by the first evaporator 230, so as to achieve the purpose of deep cooling of the refrigerant in the refrigerant flow path 210.

[0076] In some embodiments, combined Figure 1 and Figure 2 As shown, the absorption heat pump system 200 further includes a first condenser 240 and an absorber 250. The first condenser 240 is disposed between the generator 220 and the inlet end of the first evaporator 230, and the absorber 250 is disposed between the generator 220 and the outlet end of the first evaporator 230. The liquid working medium circulates among the first condenser 240, the first condenser 240, the first evaporator 230, and the absorber 250. This ensures the working performance of the absorption heat pump system 200 to a certain extent and enables the absorption heat pump system 200 to effectively perform deep cooling on the refrigerant in the refrigerant flow path 210.

[0077] In some embodiments, combined Figure 1 and Figure 2As shown, the absorption heat pump system 200 further includes a solution pump 270, which is disposed between the generator 220 and the absorber 250. The solution pump 270 is used to control the flow rate of the liquid working medium between the first condenser 240, the first condenser 240, the first evaporator 230, and the absorber 250. It should be noted that when the liquid working medium circulates between the first condenser 240, the first condenser 240, the first evaporator 230, and the absorber 250, a too fast flow rate of the liquid working medium may cause problems such as increased pressure fluctuations and increased noise in the absorption heat pump system 200; while a too slow flow rate of the liquid working medium may affect the thermal efficiency of the absorption heat pump system 200. Therefore, the present application provides a solution pump 270 to control the flow rate of the liquid working medium between the first condenser 240, the first condenser 240, the first evaporator 230, and the absorber 250. In this way, the flow rate of the liquid working medium can be adjusted during operation of the absorption heat pump system 200 to optimize the performance of the absorption heat pump system 200.

[0078] At the same time, the solution pump 270 controls the flow rate of the liquid working medium between the first condenser 240, the first condenser 240, the first evaporator 230 and the absorber 250, and accordingly controls the liquid working medium to effectively circulate between the first condenser 240, the first condenser 240, the first evaporator 230 and the absorber 250, thereby ensuring the working performance of the absorption heat pump system 200.

[0079] In some embodiments, the flow rate of the solution pump 270 can be precisely controlled by adjusting the motor speed, thereby utilizing the solution pump 270 to control the flow rate of the liquid working medium between the first condenser 240 , the first condenser 240 , the first evaporator 230 and the absorber 250 .

[0080] The motor speed can be adjusted by changing the power supply voltage or current of the motor.

[0081] In other embodiments, a regulating valve may be installed on the inlet and outlet pipes of the solution pump 270 to control the resistance of the liquid working medium by changing the opening of the regulating valve, thereby achieving the purpose of adjusting the flow rate of the liquid working medium.

[0082] In some embodiments, combined Figure 1 and Figure 2As shown, a recovery branch 280 is provided between the generator 220 and the absorber 250, and the recovery branch 280 is used to transport the concentrated solution of the liquid working medium in the generator 220 to the absorber 250. In this way, when the concentration of the liquid working medium in the generator 220 changes to form a concentrated solution, it is convenient to transport the concentrated solution to the absorber 250, which is beneficial to the subsequent mixing of the concentrated solution with the vapor, thereby facilitating the subsequent direct transport of the dilute solvent toward the generator 220 through the absorber 250, and facilitating the effective circulation of the liquid working medium among the first condenser 240, the first evaporator 230 and the absorber 250, thereby ensuring the working performance of the absorption heat pump system 200.

[0083] In some embodiments, as Figure 2 As shown, the absorption heat pump system 200 also includes an expansion valve 260, one end of the first condenser 240 is connected to the generator 220, the other end of the first condenser 240 is connected to the first evaporator 230, the first evaporator 230 is connected to the absorber 250, the absorber 250 and the generator 220 are connected to each other, and the expansion valve 260 is connected between the first condenser 240 and the first evaporator 230. When the refrigerant enters the refrigerant flow path 210 and exchanges heat with the liquid working medium in the generator 220, the liquid working medium circulation can be driven, wherein the liquid working medium here can be understood as lithium bromide-water. When the liquid working medium circulation is driven, the lithium bromide solution and the working medium vapor with different boiling points in the generator 220 are separated, and the high temperature and high pressure working medium is heated. The high-temperature and high-pressure working fluid vapor enters the first condenser 240 for heat dissipation, and the lithium bromide solution enters the absorber 250 through the recovery branch 280. When the high-temperature and high-pressure working fluid vapor enters the first condenser 240 for heat dissipation, it can be converted into a medium-temperature and high-pressure working fluid. The medium-temperature and high-pressure working fluid is throttled by the expansion valve 260 and becomes a low-temperature and low-pressure working fluid. The low-temperature and low-pressure working fluid exchanges heat with the refrigerant in the refrigerant flow path 210 in the first evaporator 230, and becomes a low-temperature and low-pressure working fluid vapor and enters the absorber 250. At the same time, the low-temperature and low-pressure working fluid vapor entering the absorber 250 and the lithium bromide concentrated solution from the generator 220 are mixed and release heat, and then pressurized and transported to the generator 220 by the solution pump 270 to enter the next refrigeration cycle.

[0084] In some embodiments, combined Figure 1 and Figure 2As shown, the refrigerant flow path 210 is connected in series with a throttling element 211 located between the generator 220 and the first evaporator 230. This means that the refrigerant flow path 210 is connected in series with the throttling element 211, and the throttling element 211 is located between the generator 220 and the first evaporator 230. In this way, after the refrigerant in the refrigerant flow path 210 is cooled in the generator 220, it can first be throttled and depressurized by the throttling element 211, and then further deeply cooled by the first evaporator 230, so as to achieve the purpose of deeply cooling the refrigerant in the refrigerant flow path 210 and ensure the cooling effect of the refrigerant to a certain extent.

[0085] The throttling element 211 mentioned here can be understood as a throttle valve.

[0086] In summary, in a specific example, especially in high-temperature areas, the thermal management system 1000 of the present application uses a large amount of high-quality heat originally used for heat dissipation of the external condenser as the driving heat source of the absorption heat pump system 200 during operation, so as to realize the circulation of the liquid working medium in the driving absorption heat pump system 200, and make the high-temperature and high-pressure refrigerant condense once in the generator 220, and then throttle and reduce the pressure in the throttling element 211, and then enter the first evaporator 230 and further exchange heat with the low-temperature and low-pressure working fluid in the absorption heat pump system 200 to achieve secondary cooling. Finally, the refrigerant enters the first heat exchange branch 120 for cabin and / or battery cooling to take away the heat of the cabin and / or battery.

[0087] In some embodiments, as Figure 1 As shown, a first control valve 130 is provided between the refrigerant flow path 210 and the exhaust port 112 of the compressor 110, for controlling the on-off connection between the refrigerant flow path 210 and the exhaust port 112 of the compressor 110. Here, the first control valve 130 is used to control the on-off connection between the refrigerant flow path 210 and the exhaust port 112 of the compressor 110, thereby facilitating control of whether the refrigerant discharged through the exhaust port 112 of the compressor 110 flows through the refrigerant flow path 210, that is, controlling whether the refrigerant in the compression heat pump system 100 is cooled by the absorption heat pump system 200, thereby reducing the difficulty of controlling the flow direction of the refrigerant.

[0088] In some embodiments, the first control valve 130 is a solenoid valve to reduce the difficulty of on-off control between the refrigerant flow path 210 and the exhaust port 112 of the compressor 110 .

[0089] In some embodiments, as Figure 1 As shown, the first heat exchange branch 120 includes a first branch 121, which is used for battery cooling. Thus, the first heat exchange branch 120 can be used for battery cooling, ensuring the working performance and safety of the battery.

[0090] In some embodiments, as Figure 1 As shown, the first heat exchange branch 120 includes a second branch 122, and the second branch 122 is used for cabin cooling. Thus, the first heat exchange branch 120 can be used for cabin cooling to ensure vehicle comfort.

[0091] In some embodiments, as Figure 1 As shown, the first heat exchange branch 120 includes a first branch 121 and a second branch 122. The first branch 121 is used for battery cooling, and the second branch 122 is used for cabin cooling. The first branch 121 and the second branch 122 are connected in parallel. This allows the first heat exchange branch 120 to cool both the cabin and the battery, ensuring both vehicle comfort and battery performance and safety.

[0092] At the same time, by arranging the first branch 121 and the second branch 122 in parallel, the first branch 121 and the second branch 122 can also be made independent of each other, that is, the battery can be cooled separately, the cabin can be cooled separately, and the battery and the cabin can be cooled simultaneously, thereby improving the flexibility of use of the thermal management system 1000.

[0093] In some embodiments, as Figure 1 As shown, first branch 121 is provided with a heat exchanger 1211 and a second control valve 1212. Heat exchanger 1211 is used for heat exchange with the battery. Second control valve 1212 is located between heat exchanger 1211 and refrigerant flow path 210 and is used to control the on / off state of first branch 121. This facilitates use of second control valve 1212 to control whether refrigerant in refrigerant flow path 210 flows through heat exchanger 1211, reducing the difficulty of controlling first branch 121 and making thermal management system 1000 more flexible.

[0094] Among them, when the refrigerant in the refrigerant flow path 210 flows through the heat exchange element 1211, heat exchange between the refrigerant and the battery is realized, thereby achieving the purpose of using the refrigerant to reduce the battery temperature; when the refrigerant in the refrigerant flow path 210 does not flow through the heat exchange element 1211, the thermal management system 1000 does not perform battery cooling work.

[0095] Optionally, the second control valve 1212 is an electronic expansion valve. In this way, while the second control valve 1212 is used to control the on and off of the first branch 121, the second control valve 1212 can also have the function of throttling and reducing pressure, so as to accurately adjust the output of the refrigerant, thereby making the thermal management system 1000 more energy-efficient and lower in energy consumption.

[0096] In a specific example, when the second control valve 1212 controls the first branch 121 to be open, Figure 1As shown, when the refrigerant in the refrigerant flow path 210 enters the first evaporator 230 and further exchanges heat with the low-temperature and low-pressure working fluid in the absorption heat pump system 200, the refrigerant with a higher degree of supercooling enters the second control valve 1212 and finally enters the heat exchange element 1211 to exchange heat with the battery to achieve the purpose of lowering the battery temperature.

[0097] It is worth noting that the heat exchange component 1211 is used to exchange heat with the battery, so that the refrigerant can be directly set in the heat exchange component 1211 to exchange heat with the battery, without coolant as an intermediate heat exchange medium, thereby achieving the purpose of cooling or heating the battery by direct cooling and heating, thereby improving the heat exchange effect.

[0098] In some embodiments, the heat exchange element 1211 is a heat exchange plate, which contacts the battery to achieve heat exchange with the battery, thereby adjusting the temperature of the battery.

[0099] Alternatively, as Figure 1 As shown, second branch 122 is provided with a second evaporator 1221 and a third control valve 1222. Second evaporator 1221 is used for heat exchange with the cabin, and third control valve 1222 is located between second evaporator 1221 and refrigerant flow path 210. Third control valve 1222 is used to control the on-off state of second branch 122. This facilitates use of third control valve 1222 to control whether refrigerant in refrigerant flow path 210 flows through second evaporator 1221, reducing the difficulty of controlling second branch 122 and making thermal management system 1000 more flexible.

[0100] Among them, when the refrigerant in the refrigerant flow path 210 flows through the second evaporator 1221, heat exchange between the refrigerant and the cabin is realized, thereby achieving the purpose of using the refrigerant to reduce the cabin temperature; when the refrigerant in the refrigerant flow path 210 does not flow through the second evaporator 1221, the thermal management system 1000 does not perform cabin cooling work.

[0101] Optionally, the third control valve 1222 is an electronic expansion valve. In this way, while the third control valve 1222 is used to control the on and off of the second branch 122, the third control valve 1222 can also have the function of throttling and reducing pressure, so as to accurately adjust the output of the refrigerant, thereby making the thermal management system 1000 more energy-efficient and lower in energy consumption.

[0102] In a specific example, when the third control valve 1222 controls the second branch 122 to be open, Figure 1As shown, after the refrigerant in the refrigerant flow path 210 enters the first evaporator 230 and further exchanges heat with the low-temperature and low-pressure working fluid in the absorption heat pump system 200, the refrigerant with a higher degree of subcooling enters the third control valve 1222 and finally enters the second evaporator 1221 to exchange heat with the cabin, thereby achieving the purpose of lowering the cabin temperature and expanding the enthalpy difference range of the refrigerant in the first evaporator 230 to achieve higher cooling efficiency.

[0103] In some embodiments, as Figure 1 As shown, the first end of the first branch 121 is switchedly connected to the air intake port 111 and the air exhaust port 112, and the second end of the first branch 121 is switchedly connected to the refrigerant flow path 210 and the air intake port 111. When the first end of the first branch 121 is connected to the air intake port 111 and the second end of the first branch 121 is connected to the refrigerant flow path 210, it is used to cool the battery. When the first end of the first branch 121 is connected to the exhaust port 112 and the second end of the first branch 121 is connected to the air intake port 111, it is used to heat the battery. What is meant here is that the first end of the first branch 121 can be connected to the air intake port 111 or to the exhaust port 112, and the second end of the first branch 121 can be connected to the refrigerant flow path 210 or to the air intake port 111, wherein, when the first end of the first branch 121 is connected to the air intake port 111 and the second end of the first branch 121 is connected to the refrigerant flow path 210, the first heat exchange branch 120 is used to cool the battery (such as Figure 4 As shown), when the first end of the first branch 121 is connected to the exhaust port 112 and the second end of the first branch 121 is connected to the intake port 111, the first heat exchange branch 120 is used to heat the battery (as shown). Figure 6 As shown), the thermal management system 1000 has both battery heating and battery cooling functions, thereby enriching the functions of the thermal management system 1000 and maintaining the battery temperature within a suitable temperature range, thereby ensuring the battery's operating performance to a certain extent, extending the battery's service life, and reducing the cost of use.

[0104] In some embodiments, combined Figure 1 、 Figure 4 and Figure 6 As shown, a fourth control valve 151 is provided between the first end of the first branch 121 and the exhaust port 112, and a fifth control valve 152 is provided between the first end of the first branch 121 and the air intake port 111. When the fourth control valve 151 is turned on and the fifth control valve 152 is turned off, the first end of the first branch 121 is connected to the exhaust port 112. When the fourth control valve 151 is turned off and the fifth control valve 152 is turned on, the first end of the first branch 121 is connected to the air intake port 111, thereby realizing the switching connection between the first end of the first branch 121 and the air intake port 111 and the exhaust port 112, and reducing the difficulty of connecting the first end of the first branch 121 with the air intake port 111 and the exhaust port 112.

[0105] In some embodiments, the fourth control valve 151 and the fifth control valve 152 are both formed as solenoid valves.

[0106] In some embodiments, combined Figure 1 、 Figure 4 and Figure 6 As shown, a first one-way valve 161 is provided between the second end of the first branch 121 and the refrigerant flow path 210, and the first one-way valve 161 is used to realize the one-way flow of the refrigerant in the refrigerant flow path 210 toward the first branch 121. A second one-way valve 162 is provided between the second end of the first branch 121 and the air intake port 111, and the second one-way valve 162 is used to realize the one-way flow of the refrigerant in the first branch 121 toward the air intake port 111, thereby realizing the switching connection between the second end of the first branch 121 and the refrigerant flow path 210 and the air intake port 111, and reducing the difficulty of connecting the second end of the first branch 121 with the refrigerant flow path 210 and the air intake port 111.

[0107] In some embodiments, as Figure 1 As shown, a sixth control valve 153 is provided between the second one-way valve 162 and the air intake port 111 to control the on-off connection between the second one-way valve 162 and the air intake port 111, that is, to control the on-off connection between the second end of the first branch 121 and the air intake port 111, thereby reducing the difficulty of control between the second end of the first branch 121 and the air intake port 111.

[0108] In some embodiments, the sixth control valve 153 is a solenoid valve.

[0109] In some embodiments, as Figure 1 As shown, the first end of the first branch 121 is provided with a seventh control valve 154, which is an electronic expansion valve. In this way, the seventh control valve 154 can be used to throttle and reduce the pressure of the refrigerant flowing through the first end of the first branch 121, thereby ensuring the heat exchange effect of the refrigerant flowing through the first branch 121 to a certain extent, and accurately adjusting the output of the refrigerant, thereby making the thermal management system 1000 more energy-efficient and lowering energy consumption.

[0110] In some embodiments, as Figure 1 As shown, the compression heat pump system 100 further includes a second heat exchange branch 140 for heating the cabin. Thus, the compression heat pump system 100 has the function of heating the cabin, further enriching the functions of the thermal management system 1000.

[0111] In some embodiments, as Figure 1As shown, second heat exchange branch 140 is provided with a second condenser 141 and an eighth control valve 142. Second condenser 141 is used for heat exchange with the cabin, and eighth control valve 142 is disposed between second condenser 141 and exhaust port 112 of compressor 110. Eighth control valve 142 is used to control the on / off state of second heat exchange branch 140. This facilitates use of eighth control valve 142 to control whether refrigerant from compressor 110 flows through second condenser 141, reducing the difficulty of controlling second heat exchange branch 140. Specifically, it enables control of whether thermal management system 1000 operates in cabin heating mode, providing flexible control of thermal management system 1000.

[0112] In the description of the present invention, the features specified as "first", "second", "third", "fourth", "fifth", "sixth", "seventh" and "eighth" may explicitly or implicitly include one or more of the features, which are used to distinguish the described features, without any order or importance.

[0113] Among them, when the refrigerant exported by the compressor 110 flows through the second condenser 141, heat exchange between the refrigerant and the cabin is realized, so as to achieve the purpose of using the refrigerant to increase the cabin temperature, thereby heating the cabin; when the refrigerant exported by the compressor 110 does not flow through the second condenser 141, the thermal management system 1000 does not perform cabin heating.

[0114] Optionally, the eighth control valve 142 is an electronic expansion valve. In this way, while the eighth control valve 142 is used to control the on and off of the second heat exchange branch 140, the eighth control valve 142 can also have the function of throttling and reducing pressure, so as to accurately adjust the output of the refrigerant, thereby making the thermal management system 1000 more energy-efficient and lower in energy consumption.

[0115] In some embodiments, as Figure 1 As shown, the second heat exchange branch 140 and the refrigerant flow path 210 are connected in parallel, so that the second heat exchange branch 140 and the refrigerant flow path 210 are independent of each other, reducing the control difficulty of the thermal management system 1000.

[0116] Of course, in some other embodiments, the second heat exchange branch 140 and the refrigerant flow path 210 may also be connected in series, which is not specifically limited here.

[0117] In some embodiments, as Figure 1 As shown, a gas-liquid separator 170 is provided at the air intake 111 of the compressor 110. The gas-liquid separator 170 is used to separate the refrigerant flowing into the compressor 110 into gas and liquid, so as to ensure that the refrigerant entering the compressor 110 is formed into a gaseous state to a certain extent, thereby avoiding the liquid refrigerant from impacting the compressor 110 to a certain extent, thereby ensuring the working performance of the compressor 110.

[0118] In some embodiments, as Figure 1 As shown, thermal management system 1000 also includes a coolant system 300 for dissipating heat from the electronic control module. Coolant system 300 and compression heat pump system 100 are in heat exchange. This facilitates using the coolant in coolant system 300 to change the temperature of the refrigerant in compression heat pump system 100, thereby achieving the purpose of using thermal management system 1000 to adjust the temperature of the vehicle cabin and the battery.

[0119] In addition, by utilizing the coolant system 300 and the compression heat pump system 100 for heat exchange, the present application can fully utilize the waste heat generated by the normal operation of the electronic control module, so that when heating the vehicle cabin and / or battery, the energy efficiency of the thermal management system 1000 can be increased, that is, the heating capacity of the thermal management system 1000 can be increased.

[0120] Optionally, the coolant system 300 is filled with coolant, and the coolant circulates in the coolant system 300. When the temperature of the coolant in the coolant system 300 is high, the coolant system 300 is used to increase the temperature of the refrigerant to achieve the purpose of heating the battery and the cabin.

[0121] Optionally, the coolant can be an environmentally friendly liquid with a high specific heat, such as water or ethylene glycol. This ensures the heat exchange effect of the coolant system 300 and dissipates heat from the electronic control module, allowing the temperature of the electronic control module to be maintained within an appropriate temperature range during operation, thereby extending the service life of the electronic control module and ensuring the operating performance of the electronic control module to a certain extent.

[0122] In some embodiments, as Figure 1 As shown, the compression heat pump system 100 includes a heat exchanger 310, which includes a first flow path and a second flow path for mutually exchanging heat. The first flow path is connected between the second heat exchange branch 140 and the intake port 111 of the compressor 110, and the second flow path is part of the coolant system 300. The refrigerant flowing through the second heat exchange branch 140 to the compressor 110 can exchange heat with the coolant in the second flow path, thereby achieving heat exchange between the coolant system 300 and the compression heat pump system 100. In this way, the coolant in the coolant system 300 can be used to change the temperature of the refrigerant in the compression heat pump system 100, fully utilizing the waste heat generated by the normal operation of the electronic control module and improving the energy efficiency of the thermal management system 1000, that is, increasing the heating capacity of the thermal management system 1000 when heating the cabin.

[0123] In some embodiments, as Figure 1As shown, the first flow path is connected between the first branch 121 and the air intake 111 of the compressor 110, so that the refrigerant flowing to the compressor 110 through the first branch 121 can exchange heat with the coolant in the second flow path, so as to realize heat exchange between the coolant system 300 and the compression heat pump system 100, and increase the heating capacity of the thermal management system 1000 when heating the battery.

[0124] In a specific example, through the above-mentioned settings, the thermal management system 1000 of the present application can realize multiple operating modes through control valve conversion, which is more suitable for high-temperature areas, that is, it is more conducive to helping the thermal management system 1000 achieve deep cooling, so that the thermal management system 1000 can be used in large trucks, buses or large transport vehicles with low-temperature storage requirements.

[0125] The various operating modes of the thermal management system 1000 of the present application are described in detail below with reference to the accompanying drawings.

[0126] in, Figure 3 FIG. 1 shows a schematic diagram of the thermal management system 1000 of the present application when operating in the first cooling mode, that is, when operating cabin cooling. Figure 3 As shown, the third control valve 1222 and the first control valve 130 are connected, the second control valve 1212, the fourth control valve 151, the fifth control valve 152, the sixth control valve 153, the seventh control valve 154 and the eighth control valve 142 are disconnected, and the high-temperature and high-pressure refrigerant discharged from the compressor 110 through the exhaust port 112 enters the refrigerant flow path 210 through the first control valve 130 to exchange heat with the liquid working medium in the generator 220, and serves as a high-temperature heat source of the absorption heat pump system 200 to drive the liquid working medium in the absorption heat pump system 200. Circulation, the refrigerant exchanges heat with the liquid working medium in the generator 220, is throttled and reduced in pressure in the throttling element 211, and then further exchanges heat with the low-temperature and low-pressure working medium fluid in the absorption heat pump system 200 through the first evaporator 230. After the heat exchange is completed, it enters the second branch 122 and is throttled and reduced in pressure through the third control valve 1222. Finally, it enters the second evaporator 1221 and exchanges heat with the cabin to achieve the purpose of cooling the cabin. The refrigerant then enters the gas-liquid separator 170 for separation. After separation, it returns to the compressor 110 to enter the next cycle.

[0127] Figure 4 FIG. 1 shows a schematic diagram of the thermal management system 1000 of the present application when operating in the second cooling mode, that is, when operating battery cooling. Figure 4As shown, the second control valve 1212, the first control valve 130, the fifth control valve 152 and the seventh control valve 154 are turned on, and the third control valve 1222, the fourth control valve 151, the sixth control valve 153 and the eighth control valve 142 are turned off. The high-temperature and high-pressure refrigerant discharged from the compressor 110 through the exhaust port 112 enters the refrigerant flow path 210 through the first control valve 130 to exchange heat with the liquid working medium in the generator 220, and serves as a high-temperature heat source of the absorption heat pump system 200 to drive the circulation of the liquid working medium in the absorption heat pump system 200. The refrigerant and the generator 220 After the liquid working medium has heat exchanged, it is throttled and reduced in pressure in the throttling element 211, and then further exchanges heat with the low-temperature and low-pressure working medium fluid in the absorption heat pump system 200 through the first evaporator 230. After the heat exchange is completed, it enters the first branch 121 and is throttled and reduced in pressure through the second control valve 1212, and finally enters the heat exchange element 1211 and exchanges heat with the battery to achieve the purpose of cooling the battery. After cooling the battery, the refrigerant passes through the seventh control valve 154 and the fifth control valve 152 in turn and enters the gas-liquid separator 170 for separation. After the separation is completed, it returns to the compressor 110 to enter the next cycle.

[0128] Figure 5 FIG. 1 shows a schematic diagram of the thermal management system 1000 of the present application when operating in the third cooling mode, that is, a schematic diagram of operating cabin cooling and battery cooling simultaneously. Figure 5 As shown, the second control valve 1212, the third control valve 1222, the first control valve 130, the fifth control valve 152 and the seventh control valve 154 are turned on, and the fourth control valve 151, the sixth control valve 153 and the eighth control valve 142 are turned off. The high-temperature and high-pressure refrigerant discharged from the compressor 110 through the exhaust port 112 enters the refrigerant flow path 210 through the first control valve 130 to exchange heat with the liquid working medium in the generator 220, and drives the liquid working medium in the absorption heat pump system 200 to circulate as a high-temperature heat source of the absorption heat pump system 200. After the refrigerant exchanges heat with the liquid working medium in the generator 220, it is throttled and depressurized in the throttling element 211, and then passes through the first evaporator 230 and the absorption heat pump system The low-temperature and low-pressure working fluid in the system 200 further exchanges heat. After the heat exchange is completed, the refrigerant enters the first branch 121 and is throttled and reduced in pressure by the second control valve 1212. Finally, it enters the heat exchange element 1211 and exchanges heat with the battery to achieve the purpose of cooling the battery. After cooling the battery, the refrigerant passes through the seventh control valve 154 and the fifth control valve 152 in turn and enters the gas-liquid separator 170 for separation. The other way enters the second branch 122 and is throttled and reduced in pressure by the third control valve 1222. Finally, it enters the second evaporator 1221 and exchanges heat with the cabin to achieve the purpose of cooling the cabin. The refrigerant then enters the gas-liquid separator 170 for separation. After the separation is completed, it returns to the compressor 110 to enter the next cycle.

[0129] Figure 6FIG. 1 shows a schematic diagram of the thermal management system 1000 of the present application when operating in the first heating mode, that is, when operating battery heating. Figure 6 As shown, the second control valve 1212, the fourth control valve 151, the sixth control valve 153 and the seventh control valve 154 are turned on, and the third control valve 1222, the first control valve 130, the fifth control valve 152 and the eighth control valve 142 are turned off. The high-temperature and high-pressure refrigerant discharged from the compressor 110 through the exhaust port 112 enters the seventh control valve 154 through the fourth control valve 151 for throttling and pressure reduction. After the throttling and pressure reduction are completed, the refrigerant enters the heat exchange element 1211 and exchanges heat with the battery to achieve the purpose of heating the battery. After heating the battery, the refrigerant passes through the second control valve 1212 and the second one-way valve 162 in turn to enter the heat exchanger 310 for heat exchange with the coolant in the coolant system 300. After the heat exchange is completed, the refrigerant enters the gas-liquid separator 170 through the sixth control valve 153 for separation. After the separation is completed, it returns to the compressor 110 to enter the next cycle.

[0130] Figure 7 FIG. 1 shows a schematic diagram of the thermal management system 1000 of the present application when operating in the second heating mode, that is, when operating cabin heating. Figure 7 As shown, the sixth control valve 153 and the eighth control valve 142 are connected, and the second control valve 1212, the third control valve 1222, the first control valve 130, the fourth control valve 151, the fifth control valve 152 and the seventh control valve 154 are disconnected. The high-temperature and high-pressure refrigerant discharged from the compressor 110 through the exhaust port 112 directly enters the second condenser 141 and the cabin for heat exchange, thereby heating the cabin. After heating the cabin, the refrigerant is throttled and reduced in pressure by the eighth control valve 142. After the throttling and pressure reduction are completed, the refrigerant enters the heat exchanger 310 to exchange heat with the coolant in the coolant system 300. After the heat exchange is completed, the refrigerant enters the gas-liquid separator 170 through the sixth control valve 153 for separation. After the separation is completed, the refrigerant returns to the compressor 110 to enter the next cycle.

[0131] Of course, in some other embodiments, the thermal management system 1000 of the present application may also operate in a combination of cooling mode and heating mode, which will not be elaborated here.

[0132] In some embodiments, the thermal management system 1000 also includes a controller, which is electrically connected to the control valves (first control valve 130, fourth control valve 151, fifth control valve 152 and sixth control valve 153) and the throttle valves (second control valve 1212, third control valve 1222, seventh control valve 154 and eighth control valve 142) respectively. The controller is used to control the on and off and opening of the throttle valves, and at the same time control the on and off of the control valves, so that the thermal management system 1000 can switch between multiple modes, improve the user experience and ensure the battery performance.

[0133] Next, a vehicle according to an embodiment of the present invention will be described.

[0134] A vehicle according to an embodiment of the present invention includes a thermal management system 1000 .

[0135] The thermal management system 1000 is the aforementioned thermal management system 1000 , and the specific structure of the thermal management system 1000 is not described in detail here.

[0136] As can be seen from the above structure, the vehicle of the embodiment of the present invention, by adopting the aforementioned thermal management system 1000, can improve the comfort of the vehicle's passenger compartment, facilitate extending the service life of the battery, and ensure the safety of battery use to a certain extent, thereby improving the driving experience.

[0137] The vehicle mentioned here can be a family car, a large truck or a passenger car, etc.

[0138] It should be noted that, because the thermal management system 1000 of the present application has a relatively high refrigeration capacity, the thermal management system 1000 can also be implemented in large transport vehicles with low-temperature storage requirements.

[0139] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0140] The thermal management system 1000 according to the embodiment of the present invention and other components of a vehicle having the same are well known to those skilled in the art and will not be described in detail here.

[0141] Throughout this specification, reference to terms such as "embodiment" or "example" indicates that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present invention. In this specification, schematic representations of these terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0142] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A thermal management system, characterized in that: include: A compression heat pump system (100) comprising a compressor (110) and a first heat exchange branch (120), wherein the first heat exchange branch (120) is used for cabin and / or battery cooling, and an air intake (111) of the compressor (110) is connected to a first end of the first heat exchange branch (120); An absorption heat pump system (200) includes a refrigerant flow path (210) and a generator (220), wherein the refrigerant flow path (210) is respectively connected to the exhaust port (112) of the compressor (110) and the second end of the first heat exchange branch (120), and a portion of the refrigerant flow path (210) is located in the generator (220) to exchange heat with a liquid working medium.

2. The thermal management system according to claim 1, characterized in that The absorption heat pump system (200) further includes a first evaporator (230), the inlet end of the first evaporator (230) being connected to the generator (220), and a portion of the refrigerant flow path (210) being located in the first evaporator (230) for heat exchange with the liquid working medium.

3. The thermal management system according to claim 2, characterized in that: The refrigerant flow path (210) is connected in series with a throttling element (211) located between the generator (220) and the first evaporator (230).

4. The thermal management system according to claim 2, characterized in that: The absorption heat pump system (200) further comprises a first condenser (240) and an absorber (250), wherein the first condenser (240) is arranged between the generator (220) and the inlet end of the first evaporator (230), and the absorber (250) is arranged between the generator (220) and the outlet end of the first evaporator (230), and the liquid working medium circulates among the first condenser (240), the first condenser (240), the first evaporator (230), and the absorber (250).

5. The thermal management system according to claim 4, characterized in that: The absorption heat pump system (200) further includes a solution pump (270), which is arranged between the generator (220) and the absorber (250). The solution pump (270) is used to control the flow rate of the liquid working medium between the first condenser (240), the first condenser (240), the first evaporator (230) and the absorber (250).

6. The thermal management system according to claim 4, characterized in that: A recovery branch (280) is provided between the generator (220) and the absorber (250), and the recovery branch (280) is used to transport the concentrated solution of the liquid working medium in the generator (220) to the absorber (250).

7. The thermal management system according to claim 1, wherein: A first control valve (130) is provided between the refrigerant flow path (210) and the exhaust port (112) of the compressor (110), and the first control valve (130) is used to control the opening and closing of the refrigerant flow path (210) and the exhaust port (112) of the compressor (110).

8. The thermal management system according to claim 1, wherein: The first heat exchange branch (120) comprises a first branch (121), and the first branch (121) is used for battery cooling.

9. The thermal management system according to claim 8, characterized in that: The first branch (121) is provided with a heat exchange component (1211) and a second control valve (1212). The heat exchange component (1211) is used for heat exchange with the battery. The second control valve (1212) is located between the heat exchange component (1211) and the refrigerant flow path (210). The second control valve (1212) is used to control the on / off of the first branch (121).

10. The thermal management system according to claim 1, wherein: The first heat exchange branch (120) includes a second branch (122), and the second branch (122) is used for cabin cooling.

11. The thermal management system according to claim 10, wherein: The second branch (122) is provided with a second evaporator (1221) and a third control valve (1222), wherein the second evaporator (1221) is used for heat exchange with the cabin, and the third control valve (1222) is located between the second evaporator (1221) and the refrigerant flow path (210), and the third control valve (1222) is used for controlling the on / off of the second branch (122).

12. The thermal management system according to claim 10, wherein: The first heat exchange branch (120) further includes a first branch (121), the first branch (121) is used for battery cooling, and the first branch (121) is connected in parallel with the second branch (122).

13. The thermal management system according to claim 8, wherein: The first end of the first branch (121) is switchedly connected to the air intake port (111) and the air exhaust port (112), and the second end of the first branch (121) is switchedly connected to the refrigerant flow path (210) and the air intake port (111). When the first end of the first branch (121) is connected to the air intake port (111) and the second end of the first branch (121) is connected to the refrigerant flow path (210), the battery is cooled. When the first end of the first branch (121) is connected to the air exhaust port (112) and the second end of the first branch (121) is connected to the air intake port (111), the battery is heated.

14. The thermal management system according to any one of claims 1 to 13, characterized in that: The compression heat pump system (100) further comprises a second heat exchange branch (140) for heating the cabin.

15. The thermal management system according to claim 14, characterized in that: The second heat exchange branch (140) and the refrigerant flow path (210) are connected in parallel.

16. The thermal management system according to claim 14, wherein: It also includes a cooling liquid system (300) for dissipating heat from the electric control module, and the cooling liquid system (300) and the compression heat pump system (100) are in heat exchange.

17. The thermal management system according to claim 16, wherein: The compression heat pump system (100) includes a heat exchanger (310), the heat exchanger (310) including a first flow path and a second flow path for mutual heat exchange, the first flow path being connected between the second heat exchange branch (140) and the air intake (111) of the compressor (110), and the second flow path being part of the coolant system (300).

18. A vehicle, characterized in that: Comprising a thermal management system according to any one of claims 1-17.

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