CN117246093A

CN117246093A - Thermal management system and vehicle

Info

Publication number: CN117246093A
Application number: CN202210644907.6A
Authority: CN
Inventors: 刘超鹏; 叶文; 陈君
Original assignee: Huawei Technologies Co Ltd
Current assignee: Huawei Technologies Co Ltd
Priority date: 2022-06-09
Filing date: 2022-06-09
Publication date: 2023-12-19
Also published as: WO2023236957A1

Abstract

The application provides a thermal management system and vehicle, through establishing ties the second heat exchanger on the second pipeline, establish ties the first heat exchanger on first pipeline, and establish ties first pipeline on the second pipeline through first pipeline section and second pipeline section, set up first multiway valve at the entry end of first pipeline section or second pipeline section, the aperture of each interface in the accessible regulation first multiway valve, make first heat exchanger and second heat exchanger during operation simultaneously, partial coolant liquid in the second pipeline can get into first pipeline, with the coolant liquid temperature that adjusts to get into first heat exchanger, make the mass flow and the temperature that wait to liquid cooling device (e.g. battery) control in suitable range, and can ensure to get into the mass flow and the temperature of second heat exchanger in suitable range, make the temperature adjustment of waiting to adjust temperature structure (e.g. passenger cabin) to suitable range, play the effect of balancing waiting liquid cooling device and waiting to adjust temperature structure, and structure's refrigerating capacity and temperature, and control method have been simplified thermal management system's structure.

Description

Thermal management system and vehicle

Technical Field

The embodiment of the application relates to the technical field of new energy electric automobiles, in particular to a thermal management system and a vehicle.

Background

Currently, electric vehicles such as pure electric vehicles are gradually popularized in the market, and thermal management technology of batteries in the pure electric vehicles is also continuously developed. Because the optimal temperature interval of the battery cell is narrow (generally 20-45 ℃), the inlet temperature of the cooling liquid and the temperature uniformity in the battery pack are particularly important in the process of heat management of the battery pack.

Taking a cooling mode as an example, in order to solve the problem of matching the temperature and the cooling capacity of an electronic device to be cooled (such as a Battery pack in an electric automobile) with other structures to be cooled (such as a passenger cabin), a conventional thermal management system may include a Condenser (condensing unit) and an air-cooled humidifier and a Battery-cooled evaporator (Battery Condenser) connected in parallel to an outlet end of the Condenser, wherein the air-cooled humidifier is located in the passenger cabin, and an inlet end of the air-cooled humidifier is communicated with the outlet end of the Condenser through a first valve, and an outlet end of the air-cooled humidifier is communicated with the inlet end of the Condenser. The battery cooling evaporator is connected in series on the battery pack loop, the inlet end of the battery cooling evaporator is communicated with the outlet end of the condenser through the second valve, one outlet end of the battery cooling evaporator is communicated with the inlet end of the battery pack, and the other outlet end of the battery cooling evaporator is communicated with the condenser. When the passenger cabin and the battery pack are refrigerated simultaneously, a first valve and a second valve can be opened, so that one part of refrigerant in the condenser enters the air cooling humidifier to cool air in the passenger cabin, the other part of refrigerant enters the battery cooling evaporator, and cooling liquid in the battery pack loop enters the battery pack after being cooled by the battery cooling evaporator so as to take away heat in the battery pack. In addition, the opening degrees of the first valve and the second valve are controlled to ensure that the temperature interval and the refrigerating capacity of the passenger cabin and the temperature interval and the refrigerating capacity of the battery pack are matched at the same time, namely, the temperature and the refrigerating capacity of the passenger cabin and the battery pack are balanced.

However, in the above thermal management system, when the fluid flowing through the first valve and the second valve is a high-pressure refrigerant, such as a refrigerant, the first valve and the second valve are typically a thermal expansion valve (Thermostatic expansion valve, TXV) or an electronic expansion valve (Electronic expansion valve, EXV), which has a relatively high cost and a relatively complex opening control, so that a cooperative control process of the first valve and the second valve in the thermal management system is relatively complex, and a complexity of a control method of the thermal management system is increased.

Disclosure of Invention

The embodiment of the application provides a thermal management system and a vehicle, wherein the thermal management system can balance the refrigerating capacity and the temperature of an electronic device to be cooled and other structures to be regulated, and the structure and the control method of the thermal management system are simple.

The embodiment of the application provides a thermal management system, including first heat exchanger, second heat exchanger, first pipeline section, second pipeline section and first multiway valve, first heat exchanger is used for with waiting the liquid cooling device heat exchange, and the entry end of first heat exchanger communicates with the exit end of first heat exchanger through first pipeline, the second heat exchanger is used for with waiting the structure heat exchange that adjusts the temperature, the entry end of second heat exchanger communicates with the exit end of second heat exchanger through the second pipeline, the entry end of first pipeline section communicates with the second pipeline, and establish ties at the exit end of second heat exchanger. The outlet end of the first pipe section is communicated with the first pipeline and is connected in series with the inlet end of the first heat exchanger. The inlet end of the second pipe section is communicated with the first pipeline and is connected in series with the outlet end of the first heat exchanger; the outlet end of the second pipe section is communicated with the second pipeline and is connected in series with the inlet end of the second heat exchanger. The first multi-way valve comprises a first interface, a second interface and a third interface, the inlet end of the first pipe section is communicated with the second pipeline through the first interface, the first multi-way valve is connected in series with the second pipeline through the second interface and the third interface, or the inlet end of the second pipe section is communicated with the first pipeline through the first interface, and the first multi-way valve is connected in series with the first pipeline through the second interface and the third interface. The first interface, the second interface and the third interface of the first multi-way valve are used for being conducted in a first working mode, so that the first pipeline and the first heat exchanger form a second pipeline, the second pipeline and the second heat exchanger form a first pipeline, cooling liquid in the first pipeline is mixed with cooling liquid in the second pipeline through the first pipeline section, cooling liquid in the second pipeline is mixed with cooling liquid in the first pipeline through the second pipeline section, and the first working mode is a mode that both the first heat exchanger and the second heat exchanger are in a heat exchange state.

According to the embodiment of the application, the second pipeline and the first pipeline are arranged in the thermal management system, the first pipeline is connected in parallel to the second pipeline through the first pipeline section and the second pipeline section, and the first multi-way valve is arranged at the inlet end of the first pipeline section and the second pipeline or is arranged at the inlet end of the second pipeline section and the first pipeline, so that the first working mode of the thermal management system, namely the mode that the first heat exchanger and the second heat exchanger work simultaneously, can be realized by opening the opening of each interface in the first multi-way valve. For example, when the first heat exchanger and the second heat exchanger work simultaneously (i.e. when the device to be cooled and the structure to be tempered heat are heated simultaneously), and the temperature of the cooling liquid in the second pipeline is higher than the temperature of the cooling liquid in the first pipeline, the first interface, the second interface and the third interface of the first multi-way valve can be opened, so that the first pipeline and the first heat exchanger form a first circulation loop, after the cooling liquid in the first circulation loop enters the first heat exchanger, the cooling liquid can exchange heat with the device to be cooled, in addition, the second pipeline and the second heat exchanger form a second circulation loop, so that the cooling liquid in the second circulation loop can exchange heat with the structure to be tempered after entering the second heat exchanger, in addition, part of the cooling liquid in the second pipeline can enter the first pipeline through the first pipe section to increase the mass flow and the temperature of the cooling liquid in the first pipeline, thereby improving the temperature of the inlet end of the first heat exchanger, enabling the first heat exchanger to cool the device (such as a battery) to a proper range, in addition, the first pipeline and the second pipeline can pass through the second heat exchanger to enter the second heat exchanger to the proper temperature of the cooling liquid, and the cooling liquid in the second circulation loop can enter the second heat exchanger to the proper temperature range, thereby improve the mass flow of the cooling liquid in the passenger cabin, and the cooling system can pass through the second heat exchanger and the heat exchanger, and the temperature of the cooling liquid can reach proper temperature of the cooling structure, and the cooling liquid can reach the proper temperature flow through the heat exchange structure, and the temperature in the second circulation loop, and the cooling system can reach the proper temperature flow and the cooling effect is guaranteed. In addition, the heat management system of the embodiment of the application is simple in structure, simple and convenient in control method and low in cost.

In one possible implementation manner, the second pipeline comprises a second auxiliary section and two second main sections, wherein the first end of one second main section is communicated with the outlet end of the second heat exchanger, the second end of one second main section is respectively communicated with the inlet end of the second auxiliary section and the inlet end of the first pipe section, the first end of the other second main section is communicated with the inlet end of the second heat exchanger, the second end of the other second main section is respectively communicated with the outlet end of the second auxiliary section and the outlet end of the second pipe section, the second pipeline is connected with a temperature control assembly and a first water pump in series, the temperature control assembly is connected with the second main section of the inlet end of the second heat exchanger in series, one end of the temperature control assembly is communicated with the inlet end of the second heat exchanger, and the other end of the temperature control assembly is communicated with the outlet end of the first water pump.

Through setting up the control by temperature change subassembly in the second pipeline for the temperature of coolant liquid in the second pipeline can be adjusted through this control by temperature change subassembly, so ensure that the temperature of second heat exchanger entry end reaches suitable scope, in this way, when waiting the liquid cooling device and waiting the temperature regulation structure and heat or refrigerate (heating for example) simultaneously, the second pipeline of thermal management system and first pipeline work simultaneously, and the target temperature of coolant liquid in the second pipeline (i.e. the target temperature of second heat exchanger entry end) is higher than the target temperature of coolant liquid in the first pipeline (i.e. the target temperature of first heat exchanger entry end), can be through the control by temperature change subassembly after the temperature of coolant liquid in the second pipeline is risen to target temperature, through the aperture of three interfaces of adjusting first multiway valve, make part coolant liquid in the second pipeline get into in the first pipeline, in order to promote the temperature and the mass flow of coolant liquid that get into the first heat exchanger in the first pipeline, make the temperature of first heat exchanger entry end reach the target temperature. In addition, when the device to be cooled is cooled or heated (for example, heating), the opening degrees of the three interfaces of the first multi-way valve can be adjusted, so that the cooling liquid flowing out of the outlet end of the first heat exchanger can enter the temperature control assembly in the second pipeline through the second pipe section, after the temperature control assembly heats the cooling liquid, the cooling liquid can flow out of the outlet end of the temperature control assembly, and the cooling liquid enters the first pipeline through part of the second main section and the first pipe section of the second pipeline and finally enters the first heat exchanger, so that the high-temperature cooling liquid entering the first heat exchanger exchanges heat with the device to be cooled. In addition, through setting up first water pump on the second main section, can reach the mass flow who adjusts the coolant liquid on the second main section through adjusting the rotational speed of water pump to the mass flow of coolant liquid in the accurate control entering second heat exchanger guarantees that the coolant liquid of second heat exchanger entry end is in target temperature, guarantees to wait to adjust the temperature of temperature structure and reaches target temperature.

In a possible implementation manner, the first water pump is connected in series between the outlet end of the second pipe section and the temperature control component end, so that the power of the cooling liquid entering the temperature control component from the outlet end of the first heat exchanger through the second pipe section can be improved, namely, the reliability of the cooling liquid entering the second pipe section of the first pipeline is improved, and the part or all of the cooling liquid flowing out from the outlet end of the first heat exchanger can well enter the first main section of the second pipeline through the second pipe section when the device to be cooled is heated (or cooled) or the device to be cooled and the temperature regulating structure are heated (or cooled) simultaneously.

In a possible implementation manner, the first pipeline comprises a first auxiliary section and two first main sections, wherein the first end of one first main section is communicated with the inlet end of the first heat exchanger, the second end of one first main section is respectively communicated with the outlet end of the first auxiliary section and the outlet end of the first pipe section, the first end of the other first main section is communicated with the outlet end of the first heat exchanger, the second end of the other first main section is respectively communicated with the inlet end of the first auxiliary section and the inlet end of the second pipe section, the first pipeline is provided with a second water pump, and the second water pump is connected in series with the first main section.

In a possible implementation manner, the inlet end of the second water pump is communicated with the outlet end of the first pipe section, and the outlet end of the second water pump is communicated with the inlet end of the first heat exchanger, so that on one hand, the power of the cooling liquid entering the first pipe through the first pipe section by the second pipe can be improved, and part or all of the cooling liquid in the second pipe can well enter the first pipe.

In one possible implementation, the thermal management system of embodiments of the present application further includes an on-off valve. In some examples, the first multi-way valve is connected in series on the second pipeline, the switch valve is connected in series on the first auxiliary section, and the switch valve can ensure that the first pipeline and the first heat exchanger form a first circulation loop which is connected when the first heat exchanger and the second heat exchanger are both in operation (for example, the device to be cooled and the device to be tempered are both heated) in the first working mode, so that the cooling liquid entering the first heat exchanger can regulate the temperature of the device to be tempered. When the device to be cooled is independently heated or cooled (for example, heated), the switch valve and the port of the first multi-way valve, which are communicated with the second auxiliary section, can be closed, and the first port of the first multi-way valve and the port of the outlet end of the second main section are opened, so that the first heat exchanger, the first main section, the second main section and the second heat exchanger form a third circulation loop, namely, cooling liquid enters the temperature control assembly of the second pipeline through the outlet side pipe section and the second pipe section of the first heat exchanger to be heated, the heated cooling liquid enters the first pipeline through the first pipe section and enters the inlet end of the first heat exchanger to raise the temperature of the cooling liquid entering the first heat exchanger, and the device to be cooled is prevented from being heated to a proper range.

Or the first multi-way valve is connected in series on the first pipeline, the switch valve is connected in series on the second auxiliary section of the second pipeline, and the switch valve is conducted in the first working mode and the second working mode, namely, when the first heat exchanger and the second heat exchanger are both working (for example, the liquid cooling device and the temperature adjusting device are both used for heating), or when the second heat exchanger is independently working (for example, the temperature adjusting device is used for heating), the second pipeline and the second heat exchanger can be ensured to form a second circulation loop which is conducted, and the cooling liquid entering the second heat exchanger can be ensured to adjust the temperature of the temperature adjusting structure. When the device to be cooled is independently heated or cooled (for example, heated), the switch valve can be closed, the interface of the switch valve and the first multi-way valve, which are communicated with the first auxiliary section, can be opened, and the first interface of the first multi-way valve and the interface, which are communicated with the outlet end of the first main section, so that the first heat exchanger, the first main section, the second main section and the second heat exchanger form a third circulation loop, namely, cooling liquid enters the temperature control assembly of the second pipeline through the outlet side pipe section and the second pipe section of the first heat exchanger to be heated, then enters the first pipeline through the second heat exchanger, the first multi-way valve and the first pipe section, and enters the inlet end of the first heat exchanger, thereby increasing the temperature of the cooling liquid entering the first heat exchanger, increasing the temperature of the device to be cooled to a proper range, and avoiding that the cooling liquid flowing out through the outlet end of the first heat exchanger enters the inlet end of the first heat exchanger through the second auxiliary section and the first pipe section, but not entering the second main section to be heated, namely, avoiding the cooling liquid in the third circulation loop from being shorted at the position.

In one possible implementation, the switching valve is a one-way valve or a stop valve, so that the control procedure of the switching valve is simplified, and the cost of the switching valve is saved. For example, when the switch valve is a one-way valve and is connected in series with the second auxiliary section, in addition, when the first water pump is located at the outlet side of the second auxiliary section and the second water pump is located at the outlet side of the first auxiliary section, the rotation speed of the first water pump and the rotation speed of the second water pump can be adjusted so that in the third working mode, namely when the liquid cooling device is used for independently heating (or refrigerating), the rotation speed of the second water pump can be adjusted to be larger than the rotation speed of the first water pump, the pressure at the inlet side of the one-way valve is smaller than the pressure at the outlet side, and therefore the one-way valve can be reversely turned off, and the cooling liquid flowing out of the first pipeline is prevented from being directly shorted at the second auxiliary section and cannot enter the second pipeline for heating.

In one possible implementation manner, the first multi-way valve is a proportional three-way valve, so that the opening degrees of three interfaces of the proportional three-way valve can be adjusted according to actual needs to adjust the mass flow of the cooling liquid entering the second circulation loop from the first circulation loop, namely, the mixing water proportion in the second circulation loop, so that the temperature of the cooling liquid entering the first heat exchanger is accurately controlled, and the device to be cooled is adjusted to the target temperature. In addition, the first multi-way valve is set to be a proportional three-way valve, so that the control procedure of the first multi-way valve is simplified, and the cost of the first multi-way valve is saved.

In one possible implementation, the thermal management system of the embodiments of the present application further includes a second multi-way valve including a fourth interface, a fifth interface, a sixth interface, a seventh interface, an eighth interface, and a ninth interface. The two second main sections of the second pipeline and the second heat exchanger form temperature control pipe sections, the number of the temperature control pipe sections is two, the two temperature control pipe sections comprise a refrigerating pipe section and a heating pipe section, two ends of the heating pipe section are respectively communicated with a fourth interface and a fifth interface, and two ends of the refrigerating pipe section are respectively communicated with a sixth interface and a seventh interface; two ends of the second auxiliary section are respectively communicated with the eighth interface and the ninth interface. When the fourth interface is communicated with the ninth interface and the fifth interface is communicated with the eighth interface, two ends of the heating pipe section are communicated with two ends of the second auxiliary section. When the temperature of the structure to be regulated or the liquid cooling device to be regulated is insufficient, the corresponding interface in the second multi-way valve can be connected to switch the temperature control pipe section to the heating pipe section, so that the heating pipe section can be used for heating and raising the temperature of the cooling liquid in the second pipeline or the first pipeline so as to raise the temperature of the cooling liquid flowing through the second heat exchanger and the first heat exchanger, and the structure to be regulated or the liquid cooling device to be regulated to the target temperature. When the temperature of the structure to be regulated or the liquid cooling device to be cooled is too high, the corresponding interface in the second multi-way valve is connected to switch the temperature control pipe section into the refrigeration pipe section, so that the cooling liquid in the second pipeline or the first pipeline can be cooled through the refrigeration pipe section to reduce the temperature of the cooling liquid flowing through the second heat exchanger and the first heat exchanger, the structure to be regulated or the liquid cooling device to be cooled to the target temperature is reduced, and the whole switching process is simple and reliable in operation.

In one possible implementation, the second heat exchanger of the heating tube section is a warm air core, and the temperature control component of the heating tube section includes at least one of a condensing plate heat exchanger and an electric heating core, so as to improve the heating efficiency of the cooling liquid.

In one possible implementation, the second heat exchanger of the refrigeration tube segment is a cold air core, and the temperature control component of the refrigeration tube segment includes an evaporating plate heat exchanger to improve cooling efficiency for the cooling liquid.

In one possible implementation manner, the condensing plate heat exchanger in the heating pipe section is provided with a condensing plate heat exchange core, the evaporating plate heat exchanger in the cooling pipe section is provided with an evaporating plate heat exchange core, the inlet end of the condensing plate heat exchange core is communicated with the outlet end of the evaporating plate heat exchange core, the inlet end of the evaporating plate heat exchange core is communicated with the outlet end of the condensing plate heat exchange core, and the condensing plate heat exchange core and the evaporating plate heat exchange core are both used for circulating refrigerant, so that the recycling of the refrigerant is realized, and the cost of the thermal management system is saved.

In one possible implementation, the first heat exchanger is a battery pack cold plate, and the battery pack cold plate is in thermal contact with a battery of the battery pack, that is, the thermal management system of the embodiment of the application can realize temperature control of the battery pack.

The embodiment of the application also provides a vehicle, including battery and above thermal management system, the first heat exchanger of first pipeline in the thermal management system and battery thermal contact to realize the temperature control to the battery, ensure that the battery is in suitable temperature, in addition, through setting up above-mentioned thermal management system in the vehicle, on the one hand, can balance the refrigerating output and the temperature of waiting to adjust temperature structure and battery in the vehicle, improved thermal management system's work efficiency, reduced the consumption of vehicle, on the other hand, thermal management system's control process is simple controllable, with low costs.

In a possible implementation manner, the vehicle of the embodiment of the application further includes a passenger cabin, the second heat exchanger in the second pipeline in the thermal management system is located in the passenger cabin, that is, the structure to be tempered may be the passenger cabin, the second heat exchanger in the management system may implement temperature control in the passenger cabin so as to ensure that the temperature in the passenger cabin is in a suitable range, in addition, the thermal management system of the embodiment of the application may implement balanced distribution of refrigerating capacity and temperature of the passenger cabin and the battery, and also simplify the structure and control method of the thermal management system, and save the cost of the thermal management system.

Drawings

FIG. 1 is a schematic diagram of one of the thermal management systems provided in one embodiment of the present application;

FIG. 2 is a schematic illustration of another configuration of a thermal management system according to an embodiment of the present application;

FIG. 3 is a first state diagram of a first mode of operation of the thermal management system corresponding to FIG. 1;

FIG. 4 is a second state diagram of a first mode of operation of the thermal management system corresponding to FIG. 1;

FIG. 5 is a schematic diagram of a second mode of operation of the thermal management system corresponding to FIG. 1;

FIG. 6 is a schematic diagram of a third mode of operation of the thermal management system corresponding to FIG. 1;

FIG. 7 is a first state diagram of a first mode of operation of the thermal management system corresponding to FIG. 2;

FIG. 8 is a second state diagram of a first mode of operation of the thermal management system corresponding to FIG. 2;

FIG. 9 is a schematic diagram of a second mode of operation of the thermal management system corresponding to FIG. 2;

FIG. 10 is a schematic diagram of a third mode of operation of the thermal management system corresponding to FIG. 2;

FIG. 11 is a schematic diagram illustrating a first state in which a first operation mode of the thermal management system of FIG. 1 is a heating mode;

FIG. 12 is a schematic diagram illustrating a second state in which a first operation mode of the thermal management system of FIG. 1 is a heating mode;

FIG. 13 is a schematic diagram of a second mode of operation of the thermal management system of FIG. 1 in a heating mode;

FIG. 14 is a schematic diagram of a third mode of operation of the thermal management system of FIG. 1 in a heating mode;

FIG. 15 is a first state diagram of the first mode of operation of the thermal management system of FIG. 1 in a cooling mode;

FIG. 16 is a second state diagram of the first mode of operation of the thermal management system of FIG. 1 in a cooling mode;

FIG. 17 is a schematic diagram of a second mode of operation of the thermal management system of FIG. 1 in a cooling mode;

FIG. 18 is a schematic diagram of a third mode of operation of the thermal management system of FIG. 1 in a cooling mode;

FIG. 19 is a schematic diagram of yet another embodiment of a thermal management system according to the present application.

Reference numerals illustrate:

10-a device to be cooled; 20-a structure to be regulated; 30-a first heat exchanger; 40-a second heat exchanger;

100-a first pipeline; 200-a second pipeline; 300-a first pipe section; 400-a second pipe section; 500-a first multi-way valve; 600-switching valve; 700-a second multi-way valve; 800-a third pipeline; 900-fourth pipeline; 1000-fifth pipeline;

101-a first circulation loop; 201-a second circulation loop; 301-a third circulation loop; 110a, 110 b-a first main section; 120-a first sub-section; 210a, 210 b-a second main section; 220-a second sub-section; 510-a first interface; 520-second interface; 530-a third interface; 600 a-one-way valve; 600 b-shut-off valve; 710-fourth interface; 720-fifth interface; 730-sixth interface; 740-seventh interface; 750-eighth interface; 760-ninth interface; 770-tenth interface; 780-eleventh interface; 790-twelfth interface; 810-a third water pump; 910-a heat sink; 1100-a power assembly; 1200-fourth water pump;

2011-a temperature control pipe section; 201 a-heating a pipe section; 201 b-a refrigeration tube section; 111-a second water pump; 211-a temperature control assembly; 212-a first water pump;

40 a-warm air core; 211 a-condensing plate heat exchanger; 221 a-an electrical heating core; 40 b-a cold air core; 211 b-evaporating plate heat exchanger.

Detailed Description

The terminology used in the description section of the present application is for the purpose of describing particular embodiments of the present application only and is not intended to be limiting of the present application.

FIG. 1 is a schematic diagram of one of the thermal management systems according to one embodiment of the present application. Referring to fig. 1, an embodiment of the present application provides a vehicle including a battery (for example, a device to be cooled 10 in fig. 1) and a thermal management system, where a first heat exchanger 30 in the thermal management system is in thermal contact with the battery, so that heat exchange is performed between the battery and the first heat exchanger 30, so as to control the temperature of the battery within a first target temperature, thereby prolonging the service life of the battery and ensuring normal use of the battery.

The first target temperature is understood to be the optimum service temperature of the battery, i.e., the temperature at which the operating performance of the battery is optimal. In some examples, the first target temperature of the battery is, for example, 0 ℃ to 60 ℃ during winter, e.g., the first target temperature of the battery may be a suitable temperature value of 0 ℃, 20 ℃, 30 ℃, 40 ℃, or 60 ℃ during winter. In other examples, the first target temperature of the battery is, for example, 15 ℃ to 20 ℃ in summer, e.g., the first target temperature of the battery may be a suitable temperature value of 15 ℃, 16 ℃, 17 ℃, 18 ℃, or 20 ℃ in summer.

It should be noted that thermal contact refers to a physical contact between two components in which heat exchange can occur, in other words, heat can be transferred to each other through a position where the two components are in contact after the two components are in contact. For example, thermal contact between the first heat exchanger 30 and the battery means that after the first heat exchanger 30 contacts the battery, heat can be transferred to each other through a location where the first heat exchanger 30 contacts the battery, so that the temperature of the battery is adjusted to a first target temperature.

In some examples, the first heat exchanger 30 may be a battery pack cold plate. In practice, the battery pack cold plate and battery may be assembled or integrated together and used as a battery pack for a vehicle.

The vehicles provided by the present embodiment may include, but are not limited to, electric vehicles/vehicles (EVs), pure electric vehicles (PEV/BEV), hybrid Electric Vehicles (HEV), range-extended electric vehicles (REEV), plug-in hybrid electric vehicles (PHEV), new energy vehicles (New Energy Vehicle), and the like.

Taking an electric automobile as an example, the battery in the battery pack can provide electric energy for a motor of the electric automobile, and the motor converts the electric energy into mechanical energy, so that the electric automobile can provide capacity, and the electric automobile can normally run.

In order to prolong the endurance mileage of the electric automobile, the energy density of the unit mass of the battery core in the battery and the battery capacity of each trolley are also continuously improved, and the heat dissipation requirement of the battery in the battery pack is also increased. In addition, the optimal use temperature interval of the battery is relatively narrow, so that when the battery is in thermal management, the heat dissipation technology of the battery is developed from air cooling to liquid cooling, and the low-temperature radiator at the front end naturally dissipates heat to air conditioner low-temperature cooling liquid. For example, the cells of the battery pack are the device to be liquid cooled 10, and the battery pack cooling plate may have a channel therein, which is in thermal contact with the cells, into which a cooling liquid flows, and through the inner wall of which heat exchange occurs with the cells, thereby controlling the temperature of the cells to a first target temperature.

Of these, the inlet temperature of the cooling fluid is particularly important. It is understood that the inlet temperature of the cooling fluid refers to the temperature at which the cooling fluid enters the inlet end of the cold plate of the battery pack (i.e., the first heat exchanger 30 of the present embodiment). When the inlet temperature of the cooling liquid reaches the second target temperature, the temperature of the battery can be adjusted to the first target temperature through the battery pack cooling plate.

For example, in summer, the battery needs to be cooled, and the second target temperature of the coolant may be 15 ℃ to 20 ℃, so that the coolant at that temperature may reduce the temperature of the battery to 15 ℃ to 20 ℃. Illustratively, when the first target temperature of the battery is 20 ℃, the second target temperature of the coolant may be a suitable temperature value of 15 ℃, 16 ℃, 18 ℃, 20 ℃, or the like.

Similarly, during winter, the battery needs to be heated, and the second target temperature of the cooling liquid can be 0-40 ℃, so that the cooling liquid at the temperature can raise the temperature of the battery to 0-40 ℃. Illustratively, when the first target temperature of the battery is 40 ℃, the second target temperature of the coolant may be a suitable temperature value of 30 ℃, 35 ℃, 40 ℃, or the like.

In practice, in a vehicle such as an electric vehicle, in addition to the temperature of the battery, the temperature of other structures 20 to be tempered, such as the passenger compartment, needs to be strictly controlled, and the temperature of the passenger compartment needs to be thermally managed so that the temperature of the passenger compartment is at the third target temperature. It is understood that the third target temperature refers to a suitable temperature of the structure 20 to be tempered, such as the passenger compartment, such that comfort of passengers in the vehicle is ensured. In some examples, the third target temperature of the passenger compartment is 40-80 ℃ during winter, for example, the third target temperature of the passenger compartment may be a suitable temperature value of 40 ℃, 50 ℃, 60 ℃, 70 ℃, or 80 ℃ or the like. In other examples, the third target temperature of the passenger compartment may be, for example, 0 ℃ to 8 ℃ during summer, e.g., the third target temperature of the passenger compartment may be a suitable temperature value of 0 ℃, 3 ℃, 5 ℃, 7 ℃, or 8 ℃ or the like.

To ensure that the passenger compartment temperature is within the third target temperature, in some examples, the thermal management system may include a heat exchange core disposed within the passenger compartment having a refrigerant (e.g., a refrigerant) therein, through which heat exchange between the refrigerant and air around the heat exchange core may be achieved after the refrigerant flows into the heat exchange core, the heat exchanged air may be blown into a space of the passenger compartment by a fan or the like, such that the temperature within the passenger compartment is controlled to the third target temperature. For example, when the passenger cabin is refrigerated, the cooled refrigerant can be transmitted into the heat exchange core body, so that the refrigerant exchanges heat with the air around the heat exchange core body, the temperature of the air around the heat exchange core body is reduced, and the cooled air is blown to the inner space of the passenger cabin by the fan.

It will be appreciated that the inlet temperature of the refrigerant used to regulate the temperature of the passenger compartment may be regulated to the third target temperature by the heat exchange core when the fourth target temperature is reached. Wherein the inlet temperature of the refrigerant refers to the temperature of the refrigerant at the inlet end of the heat exchange core.

For example, in summer, the passenger compartment may be cooled, and the fourth target temperature of the refrigerant may be 0-8 ℃, so that the coolant at that temperature may reduce the temperature of the battery to 0-8 ℃. Illustratively, when the third target temperature of the passenger compartment is 8 ℃, the fourth target temperature of the refrigerant may be a suitable temperature value of 0 ℃, 3 ℃, 5 ℃, 8 ℃, etc.

Similarly, during winter, the passenger cabin needs to be heated, and the fourth target temperature of the refrigerant can be 40-80 ℃, so that the cooling liquid at the temperature can reduce the temperature of the passenger cabin to 40-80 ℃. Illustratively, when the third target temperature of the passenger compartment is 40 ℃, the fourth target temperature of the refrigerant may be a suitable temperature value of 40 ℃, 50 ℃, 60 ℃, 80 ℃, or the like.

Currently, in order to achieve simultaneous matching of the temperature and the cooling capacity of the structure to be tempered 20 (for example, the passenger cabin) and the device to be cooled 10 (for example, the battery), that is, on one hand, the matching of the temperature and the cooling capacity of the passenger cabin, and on the other hand, the matching of the temperature and the cooling capacity of the battery, in other words, in order to balance the temperature and the cooling capacity of the structure to be tempered 20 (for example, the passenger cabin) and the device to be cooled 10 (for example, the battery), the thermal management system needs to introduce more control units, which results in a complicated management method of the thermal management system.

Taking refrigeration as an example, in some embodiments, a thermal management system includes a Battery pack circulation loop, a condenser, and an air cooled humidifier and a Battery cooled evaporator (Battery condenser) connected in parallel at an outlet end of the condenser, wherein the air cooled humidifier is located within a passenger compartment and an inlet end of the air cooled humidifier is in communication with an outlet end of the condenser through a first valve and an outlet end of the air cooled humidifier is in communication with an inlet end of the condenser.

Wherein the battery cooling evaporator is connected in series on the battery pack circulation loop, the inlet end of the battery cooling evaporator is communicated with the outlet end of the condenser through the second valve, one outlet end (such as a first outlet end) of the battery cooling evaporator is communicated with the inlet end of the battery pack, and the other outlet end (such as a second outlet end) of the battery cooling evaporator is communicated with the condenser.

When the passenger cabin and the battery pack are refrigerated simultaneously, a first valve and a second valve can be opened, so that part of refrigerant in the condenser enters the air cooling humidifier, heat exchange is carried out between the refrigerant and cooling liquid (such as tap water) in the air cooling humidifier, the temperature of the tap water is reduced, the tap water is processed into water mist and sprayed into the passenger cabin to cool the air in the passenger cabin, the other part of refrigerant enters the battery cooling evaporator and heat exchange is carried out between the refrigerant and the cooling liquid entering the battery cooling evaporator in the battery pack circulation loop, the temperature of the cooling liquid is reduced, the cooled cooling liquid enters the battery pack to take away heat of the battery pack (such as a battery), and refrigeration treatment of the battery pack is realized.

In addition, the opening degree of the first valve and the opening degree of the second valve are controlled to ensure that the temperature and the refrigerating capacity of the passenger cabin and the temperature interval and the refrigerating capacity of the battery pack are matched at the same time, so that the temperature of the passenger cabin reaches a third target temperature, and the temperature of the battery pack reaches the first target temperature, namely the temperature and the refrigerating capacity of the passenger cabin and the battery pack are balanced.

However, in the above thermal management system, the fluid flowing through the first valve and the second valve is a high-pressure refrigerant, such as a refrigerant, and the first valve and the second valve are typically thermal expansion valves or electronic expansion valves, which has high cost and complex opening control, so that the cooperative control process of the first valve and the second valve in the thermal management system is complex, and the complexity of the control method of the thermal management system is increased.

In still other examples, the thermal management system may include a battery pack circulation loop and a passenger compartment circulation loop, a battery pack cold plate of the battery pack being connected in series in the battery pack circulation loop, the temperature of the coolant entering the battery pack cold plate being brought to a second target temperature by controlling the temperature of the coolant in the battery pack circulation loop to regulate the temperature of the battery to within a first target temperature range. The heat exchange core body for adjusting the temperature of the passenger cabin is connected in series in the passenger cabin circulation loop, and the temperature of the cooling liquid entering the heat exchange core body reaches a fourth target temperature by controlling the temperature of the cooling liquid in the passenger cabin circulation loop so as to adjust the temperature of the passenger cabin to be within a third target temperature range.

The passenger cabin circulation loop is connected with an intermediate heat exchanger in parallel through a three-way valve and other switching pieces, and the intermediate heat exchanger comprises a first heat exchange channel and a second heat exchange channel which are in thermal contact. The first heat exchange channel is arranged in parallel with the passenger compartment circulation loop, for example, one end (such as an inlet end) of the first heat exchange channel can be communicated with the passenger compartment circulation loop through a first interface of a three-way valve and communicated with an outlet end of the heat exchange core, the three-way valve is connected in series with the passenger compartment circulation loop through a second interface and a third interface, for example, the second interface of the three-way valve is communicated with the outlet end of the heat exchange core, and the third interface of the three-way valve is communicated with the inlet end of the heat exchange core. The other end (e.g., the outlet end) of the first heat exchange channel communicates with the passenger compartment circulation loop and with the inlet end of the heat exchange core.

The second heat exchange channel of the intermediate heat exchanger is connected in series with the battery pack circulation loop, for example, one end (such as an inlet end) of the second heat exchange channel is communicated with the outlet end of the battery pack cold plate, and the other end (such as the outlet end) of the second heat exchange channel is communicated with the inlet end of the battery pack cold plate.

In practice, when the passenger compartment and the battery compartment are cooled, the third target temperature of the passenger compartment is lower than the first target temperature of the battery pack, and correspondingly, the fourth target temperature of the cooling liquid in the passenger compartment circulation loop is lower than the second target temperature of the cooling liquid in the battery pack circulation loop.

When the passenger cabin and the battery cabin are heated, the third target temperature of the passenger cabin is higher than the first target temperature of the battery pack, and correspondingly, the fourth target temperature of the cooling liquid in the passenger cabin circulation loop is higher than the second target temperature of the cooling liquid in the battery pack circulation loop.

Therefore, when the temperature of the cooling liquid in the battery pack circulation loop is too high or too low, the three interfaces of the three-way valve can be opened, so that part of the cooling liquid in the passenger cabin circulation loop enters the first heat exchange channel of the intermediate heat exchanger and exchanges heat with the cooling liquid in the second heat exchange channel, the temperature of the cooling liquid in the battery pack circulation loop is regulated to reach the second target temperature range, and the temperature of the battery is ensured to reach the first target temperature range.

For example, when the temperature of the cooling liquid in the battery pack circulation loop is insufficient, three interfaces of the three-way valve can be opened, so that part of the cooling liquid in the passenger cabin circulation loop enters the first heat exchange channel of the intermediate heat exchanger and exchanges heat with the cooling liquid in the second heat exchange channel to raise the temperature of the cooling liquid in the battery pack circulation loop to be within a second target temperature range, and the temperature of the battery is ensured to be within the first target temperature range.

However, the intermediate heat exchanger has a heat transfer temperature difference, and the heat transfer efficiency is low, which increases the power consumption of the thermal management system.

To this end, the embodiment of the present application provides a thermal management system, by providing two pipelines, such as a second pipeline 200 and a first pipeline 100, wherein a second heat exchanger 40 connected in series on the second pipeline 200 is used for heat exchange with air in a structure 20 to be tempered, such as a passenger cabin, that is, for temperature adjustment in the passenger cabin, a first heat exchanger 30 connected in series on the first pipeline 100 is used for heat exchange with a device 10 to be liquid cooled, such as a battery, that is, for temperature adjustment in the battery, by introducing cooling liquid into the two pipelines, and connecting two ends of the first heat exchanger 30 of the first pipeline 100 to the second pipeline 200 in parallel through two pipe sections, and then matching a three-way valve provided at an inlet end of one pipe section (such as the first pipe section 300) or an inlet end of the other pipe section (such as the second pipe section 400), so that each interface of the three-way valve can be opened in the first operation mode, so that part of the cooling liquid on the second pipeline 200 can enter the first pipeline 100 through the first pipeline section 300 to increase the mass flow rate and the temperature of the cooling liquid entering the first heat exchanger 30, namely, the temperature of the cooling liquid entering the second heat exchanger 40 is regulated in a water mixing mode, thereby playing a role in regulating the temperature of the device 10 to be cooled, in addition, part of the cooling liquid flowing out of the first heat exchanger 30 can enter the second pipeline 200 through the second pipeline section 400, thereby ensuring that the mass flow rate and the temperature of the cooling liquid entering the second heat exchanger 40 are not influenced and ensuring that the temperature of the structure 20 to be cooled is within the target temperature, on one hand, the simultaneous matching of the refrigerating capacity and the temperature of the structure 20 to be cooled and the device 10 to be cooled is realized, and on the other hand, the whole thermal management system has simple structure and simple and controllable method, the temperature of the cooling liquid in the first pipeline is regulated in a water mixing mode, so that the temperature regulation efficiency of the cooling liquid in the first circulation loop is improved, the heat exchange efficiency of the heat management system is improved, and the power consumption is reduced.

The thermal management system provided in the embodiments of the present application is described in detail below with reference to the accompanying drawings.

Referring to fig. 1, an embodiment of the present application provides a thermal management system including a first heat exchanger 30, a second heat exchanger 40, a first pipe 100, a second pipe 200, a first pipe segment 300, and a second pipe segment 400.

Wherein both ends of the second pipe 200 are respectively connected to the inlet end and the outlet end of the second heat exchanger 40, i.e. the inlet end and the outlet end of the second heat exchanger 40 are connected through the second pipe 200, so that the second pipe 200 and the second heat exchanger 40 form a circulation loop (e.g. the second circulation loop 201, which will be mentioned later) in one of the operation modes (e.g. the first operation mode). The second heat exchanger 40 is used for performing heat exchange with the structure to be temperature-adjusted 20, that is, the cooling liquid entering the second heat exchanger 40 performs heat exchange with the structure to be temperature-adjusted 20 through the second heat exchanger 40, so as to adjust the temperature of the structure to be temperature-adjusted 20, so that the structure to be temperature-adjusted 20 is within a third target temperature.

Referring to fig. 1, both ends of the first pipe 100 are respectively communicated with an inlet end and an outlet end of the first heat exchanger 30, in other words, the inlet end and the outlet end of the first heat exchanger 30 are communicated through the first pipe 100, so that the first heat exchanger 30 and the first pipe 100 form another circulation circuit (for example, a first circulation circuit 101 to be mentioned later) in one of operation modes (for example, a first operation mode). The first heat exchanger 30 is configured to exchange heat with the device 10 to be cooled, for example, the cooling liquid entering the first heat exchanger 30 exchanges with the device 10 to be cooled through the first heat exchanger 30 to adjust the temperature of the device 10 to be cooled, so that the temperature of the device 10 to be cooled reaches the first target temperature.

With continued reference to fig. 1, the inlet end of the first tube segment 300 communicates with the second tube 200 and is connected in series with the outlet end of the second heat exchanger 40, and the outlet end of the first tube segment 300 communicates with the first tube 100 and is connected in series with the inlet end of the first heat exchanger 30.

The inlet end of the second pipe section 400 is connected in series with the first pipe 100 and the outlet end of the first heat exchanger 30, and the outlet end of the second pipe section 400 is connected in series with the inlet end of the second heat exchanger 40 and the second pipe 200.

For convenience of description, a portion of the pipe section of the second pipeline 200 may be referred to as a second main section, and another portion of the pipe section may be referred to as a second sub-section 220. For example, the second conduit 200 may comprise a second main section and a second secondary section 220, wherein the second main section has two, one end of the two second main sections being in communication with the inlet and outlet ends of the second heat exchanger 40, respectively, and the other end of the two second main sections being in communication with both ends of the second secondary section 220, respectively.

Referring to fig. 1, in particular, a first end of one of the second main sections (e.g., the second main section 210 a) communicates with an outlet end of the second heat exchanger 40, and a second end of the second main section 210a (see b1 in fig. 1) communicates with an inlet end of the second auxiliary section 220 and an inlet end of the first pipe section 300, respectively, such that the first pipe section 300 communicates with the outlet end of the second heat exchanger 40 through the second main section 210a and also the outlet end of the second heat exchanger 40 communicates with the second auxiliary section 220 through the second main section 210 a.

The first end of the other second main section (e.g., the second main section 210 b) communicates with the inlet end of the second heat exchanger 40, and the second end (shown with reference to a1 in fig. 1) of the second main section 210b communicates with the outlet end of the second sub-section 220 and the outlet end of the second pipe section 400, respectively, such that the outlet end of the second pipe section 400 communicates with the inlet end of the second heat exchanger 40 through the second main section 210b and also such that the inlet end of the second heat exchanger 40 communicates with the second sub-section 220 through the second main section 210 b.

In some examples, the first end of the second main section 210a is the inlet end of the second main section 210a, the second end of the second main section 210a is the outlet end of the second main section 210a (see b1 in fig. 1), the first end of the second main section 210b is the outlet end of the second main section 210b, and the second end of the second main section 210b is the inlet end of the second main section 210b (see a1 in fig. 1).

With reference to fig. 1, accordingly, a portion of the pipe segment of the first pipeline 100 may be referred to as a first main segment, and another portion of the pipe segment may be referred to as a first sub-segment 120. For example, the first conduit 100 may include a first main section and a first sub-section 120, wherein the first main section has two, one end of the two first main sections communicates with the inlet and outlet ends of the first heat exchanger 30, respectively, and the other end of the two first main sections communicates with both ends of the first sub-section 120, respectively.

With continued reference to fig. 1, specifically, a first end of one of the first main sections (e.g., first main section 110 a) communicates with the inlet end of the first heat exchanger 30, and a second end of the first main section 110a (see fig. 1 a 2) communicates with the outlet end of the first secondary section 120 and the outlet end of the first tube section 300, respectively, such that the first tube section 300 communicates with the inlet end of the first heat exchanger 30 through the first main section 110a and also such that the inlet end of the first heat exchanger 30 communicates with the outlet end of the first secondary section 120 through the first main section 110 a.

A first end of another first main section (e.g., first main section 110 b) communicates with the outlet end of first heat exchanger 30, and a second end (shown with reference to b2 in fig. 1) of first main section 110b communicates with the inlet end of first sub-section 120 and the inlet end of second pipe section 400, respectively, such that the inlet end of second pipe section 400 communicates with the outlet end of first heat exchanger 30 through first main section 110b and such that the outlet end of first heat exchanger 30 communicates with the inlet end of first sub-section 120 through first main section 110 b.

In some examples, the first end of the first main section 110a is the outlet end of the first main section 110a, the second end of the first main section 110a is the inlet end of the first main section 110a (see a2 in fig. 1), the first end of the first main section 110b is the inlet end of the first main section 110b, and the second end of the first main section 110b is the outlet end of the first main section 110b (see b2 in fig. 1).

As such, the cooling fluid flowing from the second primary section 210a may selectively flow into at least one of the second secondary section 220 and the first tube section 300, and likewise, the cooling fluid flowing from the first primary section 110 (e.g., the first primary section 110 b) at the outlet end of the first heat exchanger 30 may selectively flow into at least one of the first secondary section 120 and the second tube section 400.

It should be noted that, the inlet end and the outlet end of the embodiments of the present application are only named for the openings at two ends of the pipe section, the pipeline, the main section, the auxiliary section, or the heat exchanger, and the like, by taking the flow direction of the cooling liquid in some working modes as a reference, and are only used for distinguishing two different ports of the pipe section and the like. In some examples, the inlet and outlet ports are simply ports of a device or conduit and are not used as outlets and outlets for the cooling fluid, as will be described in detail below.

In some examples, the length of the first pipe segment 300 may be 1cm-20cm to avoid the too short length of the first pipe segment 300, so that the water mixing condition occurs at the four ports of the second end b1 of the second main segment 210a, the inlet end of the second sub-segment 220, the second end a2 of the first main segment 110a, and the outlet end of the first sub-segment 120, which ensures that the first pipeline 100 and the second pipeline 200 are independent from each other. For example, the length of the second tube segment 400 may be a suitable value of 1cm, 5cm, 10cm, 15cm, or 20 cm.

Likewise, the length of the second pipe section 400 may be 1cm to 20cm, so as to avoid water mixing at the four ports of the second end a1 of the second main section 210b, the outlet end of the second sub-section 220, the second end b2 of the first main section 110b, and the inlet end of the first sub-section 120, thereby ensuring that the first pipe 100 and the second pipe 200 are independent from each other. For example, the length of the second tube segment 400 may be a suitable value of 1cm, 5cm, 10cm, 15cm, or 20 cm.

With continued reference to fig. 1, the thermal management system of an embodiment of the present application further includes a first multi-way valve 500, the first multi-way valve 500 including a first interface 510, a second interface 520, and a third interface 530.

Referring to fig. 1, in one example (e.g., the first example), the first multi-way valve 500 may be in communication with the inlet end of the second pipe section 400, e.g., the first port 510 of the first multi-way valve 500 is in communication with the inlet end of the second pipe section 400, the first multi-way valve 500 is connected in series with the first pipe 100 through the second port 520 and the third port 530, e.g., the second port 520 of the first multi-way valve 500 is in communication with the inlet end of the first sub-section 120, and the third port 530 of the first multi-way valve 500 is in communication with the outlet end of the first main section 110b (see b2 in fig. 1), such that the first multi-way valve 500 is connected in series between the outlet end of the first main section 110b and the inlet end of the first sub-section 120, such that the three ports of the first multi-way valve 500 are connected to the inlet end of the second pipe section 400, the outlet end of the first main section 110b, and the inlet end of the first sub-section 120, respectively.

FIG. 2 is a schematic diagram of another embodiment of a thermal management system according to the present application. Referring to fig. 2, in another example (e.g., a second example), a first multi-way valve 500 communicates at an inlet end of a first pipe segment 300. For example, the first port 510 of the first multi-way valve 500 is in communication with the inlet end of the first pipe segment 300, the first multi-way valve 500 is connected in series to the second pipe 200 through the second port 520 and the third port 530, for example, the third port 530 of the first multi-way valve 500 is in communication with the outlet end of the second main segment 210a (see b1 in fig. 2), the second port 520 of the first multi-way valve 500 is in communication with the inlet end of the second sub-segment 220, such that the first multi-way valve 500 is connected in series between the outlet end of the second main segment 210a and the inlet end of the second sub-segment 220, such that the three ports of the first multi-way valve 500 are connected to the inlet end of the first pipe segment 300, the outlet end of the second main segment 210a, and the inlet end of the second sub-segment 220, respectively.

It can be understood that the "pipeline" and the "pipe section" in the embodiments of the present application may be simple pipelines, or may be a combined structure including a pipeline, a switch valve, a water pump, and other devices. The pipeline is a pipe structure such as a hose, a steel pipe and the like which are only used for conveying cooling liquid.

The first and second pipelines 100 and 200 may be, for example, simple pipes, or the first and second pipelines 100 and 200 may be a combination of devices including pipes and on-off valves. For example, the first and second pipes 100 and 200 may be hoses for transferring the coolant. Alternatively, the first and second pipes 100 and 200 include a hose, a water pump connected in series with the hose, and the like. The embodiments of the present application specifically do not limit the structure of the "pipeline" and the "pipe section".

In addition, the lengths of the first pipeline 100 and the second pipeline 200 in the embodiment of the present application may be adjusted according to actual needs, which is not limited in the embodiment of the present application.

In this embodiment, the cooling liquid flowing in the first heat exchanger 30, the second heat exchanger 40, the first pipeline 100 and the second pipeline 200 may be tap water, purified water, cooling oil or other liquid, and in addition, the cooling liquid is in a low-pressure liquid state in any working mode of the embodiment of the present application.

Fig. 3 is a schematic view of a first state of a first operation mode of the thermal management system corresponding to fig. 1, fig. 4 is a schematic view of a second state of the first operation mode of the thermal management system corresponding to fig. 1, fig. 5 is a schematic view of a second operation mode of the thermal management system corresponding to fig. 1, and fig. 6 is a schematic view of a third operation mode of the thermal management system corresponding to fig. 1. Referring to fig. 3 to 6, taking the first example as an example, the thermal management system of the embodiment of the present application may be in different operation modes by adjusting the opening degrees of the three interfaces of the first multi-way valve 500.

Referring to fig. 3 and 4, for example, the first port 510, the second port 520, and the third port 530 of the first multi-way valve 500 are used to be conducted in the first operation mode of the thermal management system to form the first circuit 100 and the first heat exchanger 30 into the first circulation loop 101, form the second circuit 200 and the second heat exchanger 40 into the second circulation loop 201, and mix the cooling liquid in the second circulation loop 201 with the cooling liquid in the first circulation loop 101 through the first pipe section 300, and mix the cooling liquid in the first circulation loop 101 with the cooling liquid in the second circulation loop 201 through the second pipe section 400. The first operation mode is a mode in which both the first heat exchanger 30 and the second heat exchanger 40 are in an operation state.

Specifically, referring to fig. 3 and 4, in one of the operation modes (for example, the first operation mode) of the thermal management system, the second heat exchanger 40 and the first heat exchanger 30 operate simultaneously, that is, the device to be cooled 10 and the structure to be tempered 20 need to be tempered to be within the target temperature range.

In the first state of the first operation mode, as shown in fig. 3, the first port 510 of the first multi-way valve 500 may be controlled to be closed, the second port 520 and the third port are turned on, i.e., the opening degree of the first port 510 is adjusted to be zero, the opening degrees of the second port 520 and the third port 530 are adjusted to be greater than zero, and the second pipeline 200 and the first pipeline 100 are independent of each other, i.e., neither the first pipeline section 300 nor the second pipeline section 400 participate in operation. The first pipeline 100 and the first heat exchanger 30 form a first circulation loop 101, and the cooling liquid in the first circulation loop 101 can enter the first heat exchanger 30 and exchange heat with the device 10 to be cooled, so as to adjust the temperature of the device 10 to be cooled to a first target temperature. Accordingly, the second pipeline 200 and the second heat exchanger 40 form a second circulation loop 201, and the cooling liquid in the second circulation loop 201 can enter the second heat exchanger 40 and exchange heat with the structure to be temperature-regulated 20 to regulate the temperature of the structure to be temperature-regulated 20 to a third target temperature.

Referring to fig. 4, in the second state of the first working mode, the opening degrees of the three ports in the first multi-way valve 500 may be adjusted to be greater than zero, that is, the three ports of the first multi-way valve 500 are all turned on, and the cooling liquid in the second circulation loop 201 may be split into two paths after flowing out from the second end (shown by b1 in fig. 4) of the second main section 210a, wherein one path (that is, the first part of cooling liquid in the second circulation loop 201) flows into the second sub-section 220, flows into the second heat exchanger 40 through the second main section 210b, and flows into the second main section 210a, so that the first part of cooling liquid in the second circulation loop 201 flows in the second circulation loop 201. The other path (i.e., the second part of the cooling liquid of the second circulation loop 201) flows into the first main section 110a through the first pipe section 300, is mixed with the cooling liquid in the first circulation loop 101, flows into the first heat exchanger 30 and then flows into the first main section 110b, the cooling liquid flowing out of the outlet end of the first main section 110b is divided into two paths through the first port 510 and the second port 520 of the first multi-way valve 500, one path (i.e., the first part of the cooling liquid of the first circulation loop 101) flows into the first main section 110a through the first auxiliary section 120, so that the part of the cooling liquid circulates in the first circulation loop 101, and the other path (the second part of the cooling liquid of the first circulation loop 101) flows into the second main section 210b through the second pipe section 400, is mixed with the cooling liquid flowing into the second main section 210b from the second section 220 (i.e., the first part of the cooling liquid of the second circulation loop 201), flows into the second heat exchanger 40 and then flows into the second auxiliary section 210a, and thus repeatedly circulates in the second main section 210 a.

In the first operation mode, the temperature of the cooling liquid entering the first heat exchanger 30 in the first circulation loop 101 is within the second target temperature range, so that the cooling liquid in the first heat exchanger 30 can be ensured to control the temperature of the device 10 to be cooled within the first target temperature range. The temperature of the cooling liquid entering the second heat exchanger 40 in the second circulation loop 201 is within the fourth target temperature range, so that the cooling liquid in the second heat exchanger 40 can be ensured to control the temperature of the structure 20 to be temperature-regulated within the third target temperature range.

It will be appreciated that the first mode of operation of the thermal management system is a mode in which both the first heat exchanger 30 and the second heat exchanger 40 are in operation. Wherein when the coolant temperature in the first circulation loop 101 satisfies the second target temperature, the coolant temperature in the second circulation loop 201 satisfies the fourth target temperature, and the first state of the first operation mode can be operated.

When the temperature of the cooling liquid in the second circulation loop 201 meets the fourth target temperature and the temperature of the cooling liquid in the first circulation loop 101 does not meet the second target temperature, the second state of the first operation mode may be operated to adjust the cooling liquid in the first circulation loop 101 so that the temperature of the cooling liquid entering the first heat exchanger 30 reaches the second target temperature range, thereby ensuring that the temperature of the device 10 to be cooled is within the first target temperature range.

Referring to fig. 5, as another operation mode (for example, the second operation mode), the second heat exchanger 40 is independently operated, that is, the second heat exchanger 40 is in an operation state, the first heat exchanger 30 is in a non-operation state, the opening of the first interface 510 of the three interfaces of the first multi-way valve 500 can be adjusted to be zero, the second interface 520 and the third interface 530 are adjusted to be conductive, that is, the opening is greater than zero, the second pipeline 200 and the second heat exchanger 40 are formed into a second circulation loop 201, and the cooling liquid flows in the second circulation loop 201, so that the cooling liquid entering the second heat exchanger 40 exchanges heat with the structure 20 to be tempered, and the temperature of the structure 20 to be tempered is adjusted to be a third target temperature.

It will be appreciated that the second operation mode of the thermal management system is a mode in which the first heat exchanger 30 is in a non-operating state and the second heat exchanger 40 is in an operating state, for example, the temperature of the structure to be tempered 20 is insufficient or too high, and needs to be controlled within the third target temperature range, and the device to be cooled 10 is not operated, or the temperature of the device to be cooled 10 is currently within the first target temperature range, and the second operation mode of the thermal management system can be operated without tempering by the thermal management system, so as to regulate the temperature of the structure to be tempered 20, and ensure that the temperature of the structure to be tempered 20 is within the third target temperature range.

In addition, in the second mode of operation, the second conduit 200 and the first conduit 100 are independent of each other, and in some examples, the first conduit 100 and the first heat exchanger 30 may have no cooling fluid therein or may have cooling fluid therein. When the first line 100 has a cooling fluid therein, the cooling fluid may be stationary or flowing within the first line 100 and the first heat exchanger 30, but not in heat exchange with the device 10 to be cooled.

It should be noted that in the second operation mode, since the cooling liquid does not flow in or out from both ends of the first pipe segment 300 and the second pipe segment 400, the inlet end and the outlet end of the first pipe segment 300 and the second pipe segment 400 are only used to distinguish between different ports of the first pipe segment 300 and the second pipe segment 400, and do not correspond to the port into which the cooling liquid enters or the port from which the cooling liquid flows. Similarly, no cooling liquid or no cooling liquid flows in the first pipeline 100 and the first heat exchanger 30 at will in the first pipeline 100 and the first heat exchanger 30, and then the inlet end and the outlet end of the first pipeline 100 and the first heat exchanger 30 are only used for distinguishing different ports of the first pipeline 100 and the first heat exchanger 30, and do not correspond to the port where the cooling liquid enters or the port where the cooling liquid flows out.

Referring to fig. 6, as still another operation mode (e.g., a third operation mode), the first heat exchanger 30 is independently operated, i.e., the first heat exchanger 30 is in an operation state, the second heat exchanger 40 is in a non-operation state, the opening of the third port 530 of the three ports of the first multi-way valve 500 is adjusted to be zero, the first port 510 and the second port 520 are adjusted to be conductive, i.e., the opening is larger than zero, the first heat exchanger 30, the two first main sections 110, the second pipe sections 400, the second heat exchanger 40, the two second main sections 210 and the first pipe sections 300 form a third circulation loop 301, and the cooling liquid can circulate in the third circulation loop 301, for example, the cooling liquid flows into the first main section 110a through the first pipe section 300 after flowing out of the second main section 210a, flows into the first main section 110b through the first heat exchanger 30 and the first main section 110b, flows into the second main section 210b through the second pipe section 400, and then flows into the second main section 210a through the second heat exchanger 40, so that the cooling liquid flows into the second main section 210a, the first main sections 300, the second main sections 110 and the second main sections 110b and the third circulation loop 301.

It can be appreciated that the third operation mode is a mode in which the first heat exchanger 30 is in an operation state, and the second heat exchanger 40 is in a non-operation state, for example, when the temperature of the device 10 to be cooled is insufficient or too high, the device 20 to be cooled needs to be controlled within a first target temperature range, and the structure 20 to be cooled does not operate, or the temperature of the structure 20 to be cooled is currently within a third target temperature range, and the third operation mode of the thermal management system can be operated without temperature adjustment by the thermal management system, so as to adjust the temperature of the device 10 to be cooled, and ensure that the temperature of the device 10 to be cooled is within the first target temperature range.

It should be noted that in the third operation mode, since the first sub-section 120 and the second sub-section 220 are not involved in the operation, for example, no inflow and outflow of the cooling liquid in the first sub-section 120 and the second sub-section 220, the inlet end and the outlet end of the first sub-section 120 and the second sub-section 220 are only used to distinguish different ports of the first sub-section 120 and the second sub-section 220, and do not correspond to ports into which the cooling liquid enters or from which the cooling liquid exits.

Wherein in the third mode of operation the second heat exchanger 40 can be regarded as a pipe.

Fig. 7 is a schematic view of a first state of the first operation mode of the thermal management system corresponding to fig. 2, fig. 8 is a schematic view of a second state of the first operation mode of the thermal management system corresponding to fig. 2, fig. 9 is a schematic view of a second operation mode of the thermal management system corresponding to fig. 2, and fig. 10 is a schematic view of a third operation mode of the thermal management system corresponding to fig. 2. Referring to fig. 7 to 10, taking the second example as an example, the thermal management system of the embodiment of the present application may be put into different operation modes by adjusting the opening degrees of the three interfaces of the first multi-way valve 500.

Referring to fig. 7 and 8, for example, the first port 510, the second port 520, and the third port 530 of the first multi-way valve 500 are used to be conducted in the first operation mode of the thermal management system to form the first pipe 100 and the first heat exchanger 30 into the first circulation loop 101, to form the second pipe 200 and the second heat exchanger 40 into the second circulation loop 201, and to mix the cooling liquid in the second circulation loop 201 with the cooling liquid in the first circulation loop 101 through the first pipe section 300, and to mix the cooling liquid in the first circulation loop 101 with the cooling liquid in the second circulation loop 201 through the second pipe section 400. The first operation mode is a mode in which both the first heat exchanger 30 and the second heat exchanger 40 are in an operation state.

Specifically, referring to fig. 7 and 8, in one of the operation modes (for example, the first operation mode) of the thermal management system, the second heat exchanger 40 and the first heat exchanger 30 are operated simultaneously, that is, the device to be cooled 10 and the structure to be tempered 20 need to be tempered to be within the target temperature range.

In the first state of the first operation mode, as shown in fig. 7, the first port 510 of the first multi-way valve 500 may be controlled to be closed, the second port 520 and the third port are turned on, i.e., the opening degree of the first port 510 is adjusted to be zero, the opening degrees of the second port 520 and the third port 530 are adjusted to be greater than zero, and the second pipeline 200 and the first pipeline 100 are independent of each other, i.e., neither the first pipeline section 300 nor the second pipeline section 400 participate in operation. The first pipeline 100 and the first heat exchanger 30 form a first circulation loop 101, and the cooling liquid in the first circulation loop 101 can enter the first heat exchanger 30 and exchange heat with the device 10 to be cooled, so as to adjust the temperature of the device 10 to be cooled to a first target temperature. Accordingly, the second pipeline 200 and the second heat exchanger 40 form a second circulation loop 201, and the cooling liquid in the second circulation loop 201 can enter the second heat exchanger 40 and exchange heat with the structure to be temperature-regulated 20 to regulate the temperature of the structure to be temperature-regulated 20 to a third target temperature.

Referring to fig. 8, in the second state of the first operation mode, the opening degrees of the three ports in the first multi-way valve 500 may be adjusted to be greater than zero, and the cooling liquid in the second circulation loop 201 may be separated into two paths through the first port 510 and the second port 520 of the first multi-way valve 500 after flowing out from the outlet end (shown by b1 in fig. 8) of the second main section 210a, wherein one path (i.e., the first part of the cooling liquid in the second circulation loop 201) flows into the second sub-section 220, flows into the second heat exchanger 40 through the second main section 210b, and flows into the second main section 210a, so that the first part of the cooling liquid in the second circulation loop 201 flows in the second circulation loop 201. The other path (i.e., the second part of the cooling liquid in the second circulation loop 201) flows into the first main section 110a through the first pipe section 300, is mixed with the cooling liquid in the first circulation loop 101, flows into the first heat exchanger 30, then flows into the first main section 110b, and the cooling liquid flowing out of the outlet end (see b2 in fig. 8) of the first main section 110b can be divided into two paths, wherein one path (i.e., the first part of the cooling liquid in the first circulation loop 101) flows into the first main section 110a through the first auxiliary section 120, so that the part of the cooling liquid circulates in the first circulation loop 101, and the other path (the second part of the cooling liquid in the first circulation loop 101) flows into the second main section 210b through the second pipe section 400, is mixed with the cooling liquid flowing into the second main section 210b from the second auxiliary section 220 (i.e., the first part of the cooling liquid in the second circulation loop 201), flows into the second heat exchanger 40, and then flows into the second main section 210a, and so on.

Referring to fig. 9, as still another operation mode (for example, the second operation mode), the second heat exchanger 40 is independently operated, that is, the second heat exchanger 40 is in an operation state, the first heat exchanger 30 is in a non-operation state, the opening of the first interface 510 of the three interfaces of the first multi-way valve 500 can be adjusted to be zero, the second interface 520 and the third interface 530 are adjusted to be conductive, that is, the opening is greater than zero, the second pipeline 200 and the second heat exchanger 40 are formed into a second circulation loop 201, and the cooling liquid flows in the second circulation loop 201, so that the cooling liquid entering the second heat exchanger 40 exchanges heat with the structure 20 to be tempered, and the temperature of the structure 20 to be tempered is adjusted to be at a third target temperature.

In the second operation mode of the second example, the states of the first pipeline 100, the first heat exchanger 30, the first pipe section 300 and the second pipe section 400 may be directly referred to the first operation mode of the first example, which is not described herein.

Referring to fig. 10, as still another operation mode (e.g., a third operation mode), the first heat exchanger 30 is independently operated, i.e., the first heat exchanger 30 is in an operation state, the second heat exchanger 40 is in a non-operation state, the opening of the second port 520 of the three ports of the first multi-way valve 500 is adjusted to be zero, the first port 510 and the third port 530 are adjusted to be conductive, i.e., the opening is larger than zero, the first heat exchanger 30, the two first main sections 110, the second pipe sections 400, the second heat exchanger 40, the two second main sections 210 and the first pipe sections 300 form a third circulation loop 301, and the cooling liquid can circulate in the third circulation loop 301, for example, the cooling liquid flows into the first main section 110a through the first pipe section 300 after flowing out of the second main section 210a, flows into the first main section 110b through the first heat exchanger 30 and the first main section 110b, flows into the second main section 210b through the second pipe section 400, and then flows into the second main section 210a through the second heat exchanger 40, so that the cooling liquid flows into the second main section 210a, the first main sections 300, the second main sections 110 and the second main sections 110b and the third circulation loop 301.

It will be appreciated that the third mode of operation is a mode in which the first heat exchanger 30 is in an operating state and the second heat exchanger 40 is in a non-operating state. Wherein in the third mode of operation the second heat exchanger 40 can be regarded as a pipe.

In the third operation mode of the second example, the states of the first sub-segment 120 and the second sub-segment 220 may be directly referred to the first operation mode of the first example, which is not described herein.

It should be noted that, in the embodiment of the present application, when the second heat exchanger 40 and the first heat exchanger 30 are simultaneously heating, that is, when the to-be-cooled device 10 and the to-be-cooled structure 20 are both heating, the target inlet temperature (that is, the fourth target temperature) of the second heat exchanger 40 is greater than the target inlet temperature (that is, the second target temperature) of the first heat exchanger 30, that is, when the to-be-cooled structure 20 and the to-be-cooled device 10 are simultaneously heating, the third target temperature of the to-be-cooled structure 20 is greater than the first target temperature of the to-be-cooled device 10, so that, when the to-be-cooled structure 20 and the to-be-cooled device 10 are simultaneously heating, the temperature of the cooling liquid in the second circulation loop 201 is greater than the temperature of the cooling liquid in the first circulation loop 101, and when the temperature of the cooling liquid at the inlet end of the first heat exchanger 30 is insufficient, a first working mode of the thermal management system, for example, the second state of the movable first working mode can be adopted, and the opening degree of the three interfaces of the first multi-way valve 500 is all greater than zero, for example, the first interface 510, the second interface 520 and the third interface of the third interface are all can be conducted, and the second interface is enabled to be made to be higher than the first interface temperature of the first interface of the third interface, and the third interface is enabled to be made to be higher than the target temperature.

When the second heat exchanger 40 and the first heat exchanger 30 are simultaneously cooling, i.e. the to-be-cooled device 10 and the to-be-cooled device 10 are both cooling, the target inlet temperature (i.e. the fourth target temperature) of the second heat exchanger 40 is smaller than the target inlet temperature (i.e. the second target temperature) of the first heat exchanger 30, i.e. when the to-be-cooled device 10 is simultaneously cooling, the third target temperature of the to-be-cooled device 20 is smaller than the first target temperature of the to-be-cooled device 10, so that the temperature of the cooling liquid in the second circulation loop 201 is lower than the temperature of the cooling liquid in the first circulation loop 101 when the to-be-cooled device 10 is simultaneously cooling, and when the temperature of the cooling liquid at the inlet end of the first heat exchanger 30 is too high, for example, the first working mode of the thermal management system can be adopted, i.e. the second state of the first working mode can be moved, i.e. the opening degree of the three interfaces of the first multi-way valve 500 is adjusted to be larger than zero, for example, the first interface 510, the second interface 520 and the third interface 530 of the three-way valve can be conducted, so that the temperature of the cooling liquid in the second circulation loop 201 is lower than the temperature of the cooling liquid in the first circulation loop 101 and the first circulation loop is enabled to be cooled down to the target temperature.

The fourth target temperature is the temperature of the inlet end of the second heat exchanger 40, which can adjust the temperature of the structure 20 to be temperature-adjusted to the third target temperature after the cooling liquid entering the second heat exchanger 40 exchanges heat with the structure 20 to be temperature-adjusted. The second target temperature is the temperature at the inlet end of the first heat exchanger 30, at which the temperature of the device 10 to be cooled can be adjusted to the first target temperature after the cooling liquid entering the first heat exchanger 30 exchanges heat with the device 10 to be cooled.

Referring to fig. 1 and 2, in some examples, a temperature control assembly 211 may be connected in series in the second pipeline 200, the temperature control assembly 211 may be connected in series to the second main section, for example, the temperature control assembly 211 may be connected in series to the second main section 210b, one end of the temperature control assembly 211 is connected to the second end (shown in a1 of fig. 1) of the second main section 210b, and the other end of the temperature control assembly 211 is connected to the inlet end of the second heat exchanger 40, so that the temperature of the cooling liquid in the second main section 210b may be adjusted by the temperature control assembly 211 to ensure that the temperature of the cooling liquid entering the second heat exchanger 40 can be controlled within the fourth target temperature, thereby adjusting the structure to be tempered 20 within the third target temperature.

Taking the first example as an example, referring to fig. 3 and fig. 4, when both the structure to be tempered 20 and the device to be cooled 10 need to be heated, the first operation mode of the thermal management system is adopted, that is, the temperature and the mass flow rate of the cooling liquid in the second circulation loop 201 can be controlled to control the temperature of the cooling liquid entering the inlet end of the second heat exchanger 40 to reach the fourth target temperature, so that the cooling liquid at the temperature can exchange heat with the structure to be tempered 20 in the second heat exchanger 40 to heat the structure to be tempered 20.

Referring to fig. 4, when the temperature of the cooling liquid at the inlet end of the first heat exchanger 30 is insufficient, the opening degree of the three ports of the first multi-way valve 500, such as a proportional three-way valve, can be adjusted to control the mass flow rate m2 (i.e. the reference mass flow rate m 2) of the cooling liquid exchanged between the second circulation loop 201 and the first circulation loop 101, so as to achieve the effect of adjusting the mixing ratio, i.e. the duty ratio of m2 in the mass flow rate m3 of the cooling liquid in the first circulation loop 101, so as to raise the temperature of the cooling liquid in the first circulation loop 101, and the temperature at the inlet end of the first heat exchanger 30 can be adjusted to reach the second target temperature.

Specifically, when the thermal management system receives a work demand: when the fourth target temperature at the inlet end of the second heat exchanger 40 is T1, the mass flow rate is m1, the second target temperature at the inlet end of the first heat exchanger 30 is T2, and the mass flow rate is m3, the cooling liquid in the second circulation loop 201 can be controlled to have the target mass flow rate of m1 entering the second heat exchanger 40, and the cooling liquid in the first circulation loop 101 can be controlled to have the target mass flow rate of m3 entering the first heat exchanger 30.

Referring to fig. 3 and 4, when the temperature Tn of the inlet end of the second heat exchanger 40 is less than T1, the cooling liquid in the second pipe 200 may be heated by the temperature control assembly 211 such that the temperature Tn of the inlet end of the second heat exchanger 40 reaches the fourth target temperature T1, i.e., tn=t1.

Referring to fig. 3, when the temperature tb=t2 at the inlet end of the first heat exchanger 30, the first port 510 of the first multi-way valve 500 may be controlled to be closed, the second port 520 and the third port 530 are both turned on, i.e. the thermal management system is in the first state of the first operation mode, and the cooling liquid in the first circulation loop 101 and the second circulation loop 102 circulate in the respective circulation loops, i.e. the cooling liquid in the first circulation loop 101 enters the first heat exchanger 30, and then the temperature of the device 10 to be cooled may be controlled within the first target temperature range by the first heat exchanger 30.

Referring to fig. 4, when the temperature Tb at the inlet end of the first heat exchanger 30 is less than T2, the three ports of the first multi-way valve 500 are all connected, that is, the thermal management system is in the second state of the first working mode, part of the cooling liquid (for example, the cooling liquid with the mass flow of m 2) in the second circulation loop 201 may flow into the first main section 110a of the first circulation loop 101 through the first pipe section 300, be mixed with the cooling liquid in the first circulation loop 101, after entering the first heat exchanger 30, the mixed cooling liquid (with the mass flow of m 3) may be separated into two paths through the first port 510 and the second port 520 of the first multi-way valve 500 at the outlet end of the first main section 110b after entering the heat exchange with the liquid cooling device 10, one path of cooling liquid (with the mass flow of m3-m 2) may flow into the first auxiliary section 110a through the first pipe section 120, the other path of cooling liquid (with the mass flow of m 2) may flow into the second main section 210b through the second pipe section 400, flow out of the mixed cooling liquid with the second auxiliary section 220, and after entering the heat exchange with the second auxiliary cooling section 20, and after the mixed cooling liquid flows into the heat exchange component 20 after the mixed cooling liquid and the mixed cooling liquid with the second auxiliary cooling liquid enters the heat exchange structure after the heat exchange structure.

The above-mentioned cooling liquid entering the first heat exchanger 30 includes a high-temperature cooling liquid with a mass flow rate of m2 and a low-temperature cooling liquid with a mass flow rate of m1, so that compared with the cooling liquid entering the first heat exchanger 30 in the first circulation loop 101 in the first state, the duty ratio of the reference mass flow rate m2 in the mass flow rate m3 is increased, thereby raising the temperature Tb and reaching the final second target temperature T2, so that the cooling liquid entering the first heat exchanger 30 can regulate the temperature of the device 10 to be cooled to the first target temperature range.

In addition, the opening degrees of the first and second ports 510 and 520 of the first multi-way valve 500 are controlled to control the mass flow rate of the coolant flowing into the first sub-section 120 to be m3-m2, thereby ensuring that the mass flow rate of the low-temperature coolant flowing into the first main section 110a is m3-m2, so that when the high-temperature coolant having the mass flow rate of m2 in the second circulation loop 201 flows into the first main section 110a, the mass flow rate of the coolant flowing into the first heat exchanger 30 can be ensured to be m3. At the same time, the mass flow rate of the cooling liquid entering the second main section 210b from the first main section 110b is ensured to be m2, so that after the part of cooling liquid is mixed with the high-temperature cooling liquid with the mass flow rate of m1-m2 flowing out of the second auxiliary section 220, the cooling liquid with the mass flow rate of m1 can be ensured to enter the second heat exchanger 40, namely, the mass flow rate of the cooling liquid entering the second heat exchanger 40 is ensured to be m 1.

In addition, after the cooling liquid flowing from the second pipe section 400 into the second main section 210b and the cooling liquid flowing from the second sub-section 220 into the second main section 210b are mixed, the temperature Tn of the cooling liquid entering the second heat exchanger 40 can reach T1 under the heating of the temperature control assembly 211, so as to ensure that the temperature of the structure to be tempered 20 is within the third target temperature range.

The opening degree of the three ports of the first multi-way valve 500 may be adjusted to control the mass flow rate m2 of the cooling liquid flowing from the second circulation circuit 201 into the first circulation circuit 101, and to control the mass flow rate m2 of the cooling liquid flowing from the first circulation circuit 101 into the second circulation circuit 201.

In some examples, the specific value of m2 may be adjusted according to the difference between Tb and T2, for example, when the difference between Tb and T2 is larger, the opening of the first interface 510 in the first multi-way valve 500 may be increased, and the opening of the second interface 520 may be decreased to increase the specific value of m2, thereby increasing the ratio of the reference mass flow rate m2 to the mass flow rate m3, increasing the temperature of the coolant entering the first heat exchanger 30, and additionally increasing the temperature adjustment efficiency of the coolant entering the first heat exchanger 30, so as to ensure that the coolant entering the first heat exchanger 30 quickly adjusts the temperature of the device 10 to be cooled to within the first target temperature range.

Referring to fig. 3 and fig. 4, when both the structure to be tempered 20 and the device to be cooled 10 need to be cooled, the first operation mode of the thermal management system is adopted, that is, the temperature and the mass flow of the cooling liquid in the second circulation loop 201 can be controlled to control the temperature of the cooling liquid entering the inlet end of the second heat exchanger 40 to reach the fourth target temperature, so that the cooling liquid at the temperature can exchange heat with the structure to be tempered 20 in the second heat exchanger 40 to cool the structure to be tempered 20.

Referring to fig. 4, when the temperature of the cooling liquid at the inlet end of the first heat exchanger 30 is too high, the opening degree of the three ports of the first multi-way valve 500, such as the proportional three-way valve, can be adjusted to control the mass flow rate m2 (i.e. the reference mass flow rate m 2) of the cooling liquid exchanged between the second circulation loop 201 and the first circulation loop 101, so as to achieve the effect of adjusting the mixing ratio, i.e. controlling the duty ratio of m2 in the mass flow rate m3 of the cooling liquid in the first circulation loop 101, so as to reduce the temperature of the cooling liquid in the first circulation loop 101, and the temperature at the inlet end of the first heat exchanger 30 can be adjusted to reach the second target temperature.

Referring to fig. 3 and 4, in addition, when the temperature Tn of the inlet end of the second heat exchanger 40 is greater than T1, the cooling liquid in the second pipeline 200 may be cooled by the temperature control assembly 211, so that the temperature Tn of the inlet end of the second heat exchanger 40 is reduced to the fourth target temperature T1, i.e., tn=t1.

Referring to fig. 4, when the temperature Tb at the inlet end of the first heat exchanger 30 is greater than T2, the three ports of the first multi-way valve 500 are all connected, that is, the thermal management system is in the second state of the first working mode, part of the cooling fluid (e.g., the cooling fluid with the mass flow of m 2) in the second circulation loop 201 may flow into the first main section 110a of the first circulation loop 101 through the first pipe section 300, be mixed with the cooling fluid in the first circulation loop 101, after entering the first heat exchanger 30, the mixed cooling fluid (with the mass flow of m 3) may be separated into two paths through the first port 510 and the second port 520 of the first multi-way valve 500 at the outlet end of the first main section 110b after entering the heat exchange with the liquid cooling device 10, one path of cooling fluid (with the mass flow of m3-m 2) may flow into the first auxiliary section 110a through the first pipe section 120, another path of cooling fluid (with the mass flow of m 2) may flow into the second main section 210b through the second pipe section 400, flow out of the mixed cooling fluid (with the second auxiliary cooling fluid 220) after entering the heat exchange with the second auxiliary cooling fluid, and after entering the heat exchange with the heat exchange device 20, and after the mixed cooling fluid is cooled by the mixed cooling fluid and then flows into the heat exchange structure 20 after the mixed cooling fluid and the mixed cooling fluid with the second auxiliary cooling fluid and the second cooling fluid has cooled fluid and cooled fluid after the mixed cooling fluid has cooled with the cooling fluid.

The above-mentioned cooling liquid entering the first heat exchanger 30 includes a low-temperature cooling liquid with a mass flow rate of m2 and a high-temperature cooling liquid with a mass flow rate of m1, so that compared with the cooling liquid entering the first heat exchanger 30 in the first circulation loop 101 in the first state, the duty ratio of the reference mass flow rate m2 in the mass flow rate m3 is increased, thereby reducing the temperature Tb and reaching the final second target temperature T2, so that the cooling liquid entering the first heat exchanger 30 can adjust the temperature of the device 10 to be cooled to the first target temperature range.

In addition, the opening degrees of the first and second ports 510 and 520 of the first multi-way valve 500 are controlled to control the mass flow rate of the coolant flowing into the first sub-section 120 to be m3-m2, thereby ensuring that the mass flow rate of the low-temperature coolant flowing into the first main section 110a is m3-m2, so that when the high-temperature coolant having the mass flow rate of m2 in the second circulation loop 201 flows into the first main section 110a, the mass flow rate of the coolant flowing into the first heat exchanger 30 can be ensured to be m3. At the same time, the mass flow rate of the cooling liquid entering the second main section 210b is ensured to be m2, so that after the part of cooling liquid is mixed with the high-temperature cooling liquid with the mass flow rate of m1-m2 flowing out of the second auxiliary section 220, the cooling liquid with the mass flow rate of m1 can be ensured to enter the second heat exchanger 40, namely, the mass flow rate of the cooling liquid entering the second heat exchanger 40 is ensured to be m1.

In addition, after the cooling liquid flowing from the second pipe section 400 into the second main section 210b and the cooling liquid flowing from the second sub-section 220 into the second main section 210b are mixed, the temperature Tn of the cooling liquid entering the second heat exchanger 40 can reach T1 under the cooling effect of the temperature control assembly 211, so as to ensure that the temperature of the structure to be tempered 20 is within the third target temperature range.

In some examples, the specific value of m2 may be adjusted according to the difference between Tb and T2, for example, when the difference between Tb and T2 is larger, the opening of the first interface 510 may be increased by increasing the opening of the first multi-way valve 500, and the opening of the second interface 520 may be decreased to increase the specific value of m2, thereby increasing the ratio of the reference mass flow rate m2 to the mass flow rate m3, reducing the temperature of the coolant entering the first heat exchanger 30, and further increasing the temperature adjustment efficiency of the coolant entering the first heat exchanger 30, so as to ensure that the coolant entering the first heat exchanger 30 quickly adjusts the temperature of the device 10 to be cooled to within the first target temperature range.

Taking the second example as an example, referring to fig. 7 and 8, when both the structure to be tempered 20 and the device to be cooled 10 need to be heated, the first operation mode of the thermal management system is adopted, that is, the temperature and the mass flow rate of the cooling liquid in the second circulation loop 201 can be controlled to control the temperature of the cooling liquid entering the inlet end of the second heat exchanger 40 to reach the fourth target temperature, so that the cooling liquid at the temperature can exchange heat with the structure to be tempered 20 in the second heat exchanger 40 to heat the structure to be tempered 20.

Referring to fig. 7, when the temperature of the cooling liquid at the inlet end of the first heat exchanger 30 is insufficient, the opening degree of the three ports of the first multi-way valve 500, such as a proportional three-way valve, can be adjusted to control the mass flow rate m2 (i.e. the reference mass flow rate m 2) of the cooling liquid exchanged between the second circulation loop 201 and the first circulation loop 101, so as to achieve the effect of adjusting the mixing ratio, i.e. the duty ratio of m2 in the mass flow rate m3 of the cooling liquid in the first circulation loop 101, so as to raise the temperature of the cooling liquid in the first circulation loop 101, and the temperature at the inlet end of the first heat exchanger 30 can be adjusted to reach the second target temperature.

Referring to fig. 7 and 8, in addition, when the temperature Tn of the inlet end of the second heat exchanger 40 is less than T1, the cooling liquid in the second pipe 200 may be heated by the temperature control assembly 211 such that the temperature Tn of the inlet end of the second heat exchanger 40 reaches the fourth target temperature T1, i.e., tn=t1.

Referring to fig. 7, when the temperature tb=t2 at the inlet end of the first heat exchanger 30, the first port 510 of the first multi-way valve 500 may be controlled to be closed, the second port 520 and the third port 530 are both turned on, i.e. the thermal management system is in the first state of the first operation mode, and the cooling liquid in the first circulation loop 101 and the second circulation loop 102 circulate in the respective circulation loops, i.e. the cooling liquid in the first circulation loop 101 enters the first heat exchanger 30, and then the temperature of the device 10 to be cooled may be controlled within the first target temperature range by the first heat exchanger 30.

Referring to fig. 8, when the temperature Tb at the inlet end of the first heat exchanger 30 is less than T2, the three ports of the first multi-way valve 500 are all connected, i.e. the thermal management system is in the second state of the first operation mode, part of the cooling fluid (e.g. the cooling fluid with the mass flow of m 2) in the second circulation loop 201 may flow into the first main section 110a of the first circulation loop 101 through the third port 530 and the first port 510 of the first multi-way valve 500 and the first pipe section 300, mix with the cooling fluid in the first circulation loop 101, after entering the first heat exchanger 30, may be separated into two paths through the outlet end of the first main section 110b after entering the heat exchange device 10, one path of cooling fluid (e.g. the cooling fluid with the mass flow of m3-m 2) may flow into the first main section 110a through the first auxiliary section 120, the other path of cooling fluid (the mass flow of m 2) may flow into the second main section 210b through the second pipe section 400, mix with the cooling fluid (the mass flow of m 3) after entering the second auxiliary section 220, and mix with the second auxiliary cooling fluid after entering the heat exchanger 30, and mix with the second auxiliary cooling fluid after entering the heat exchanger 20, and flow into the heat exchange structure for heat exchange with the second auxiliary cooling fluid 20.

In addition, the opening degrees of the first and second ports 510 and 520 of the first multi-way valve 500 are controlled to control the mass flow rate of the coolant flowing into the first sub-section 120 to be m3-m2, thereby ensuring that the mass flow rate of the low-temperature coolant flowing into the first main section 110a is m3-m2, so that when the high-temperature coolant having the mass flow rate of m2 in the second circulation loop 201 flows into the first main section 110a, the mass flow rate of the coolant flowing into the first heat exchanger 30 can be ensured to be m3. At the same time, the mass flow rate of the cooling liquid entering the second main section 210b is ensured to be m2, so that after the part of cooling liquid is mixed with the high-temperature cooling liquid with the mass flow rate of m1-m2 flowing out of the second auxiliary section 220, the cooling liquid with the mass flow rate of m1 can be ensured to enter the second heat exchanger 40, that is, the mass flow rate of the cooling liquid entering the second heat exchanger 40 is ensured to be m 1.

Referring to fig. 7 and 8, when both the structure to be tempered 20 and the device to be cooled 10 need to be cooled, the first operation mode of the thermal management system is adopted, that is, the temperature and the mass flow of the cooling liquid in the second circulation loop 201 can be controlled to control the temperature of the cooling liquid entering the inlet end of the second heat exchanger 40 to reach the fourth target temperature, so that the cooling liquid at the temperature can exchange heat with the structure to be tempered 20 in the second heat exchanger 40 to cool the structure to be tempered 20.

Referring to fig. 7, when the temperature of the cooling liquid at the inlet end of the first heat exchanger 30 is too high, the opening degree of the three ports of the first multi-way valve 500, such as the proportional three-way valve, can be adjusted to control the mass flow rate m2 (i.e. the reference mass flow rate m 2) of the cooling liquid exchanged between the second circulation loop 201 and the first circulation loop 101, so as to achieve the effect of adjusting the mixing ratio, i.e. controlling the duty ratio of m2 in the mass flow rate m3 of the cooling liquid in the first circulation loop 101, so as to reduce the temperature of the cooling liquid in the first circulation loop 101, and the temperature at the inlet end of the first heat exchanger 30 can be adjusted to reach the second target temperature.

Referring to fig. 7 and 8, in addition, when the temperature Tn of the inlet end of the second heat exchanger 40 is greater than T1, the cooling liquid in the second pipeline 200 may be cooled by the temperature control assembly 211 such that the temperature Tn of the inlet end of the second heat exchanger 40 is reduced to the fourth target temperature T1, i.e., tn=t1.

Referring to fig. 8, when the temperature Tb at the inlet end of the first heat exchanger 30 is greater than T2, the three ports of the first multi-way valve 500 are all connected, i.e. the thermal management system is in the second state of the first operation mode, part of the cooling fluid (e.g. the cooling fluid with the mass flow of m 2) in the second circulation loop 201 may flow into the first main section 110a of the first circulation loop 101 through the third port 530 and the first port 510 of the first multi-way valve 500 and the first pipe section 300, mix with the cooling fluid in the first circulation loop 101, after entering the first heat exchanger 30, may be separated into two paths through the outlet end of the first main section 110b after entering the heat exchange device 10, one path of cooling fluid (e.g. the cooling fluid with the mass flow of m3-m 2) may flow into the first main section 110a through the first auxiliary section 120, the other path of cooling fluid (the mass flow of m 2) may flow into the second main section 210b through the second pipe section 400, mix with the cooling fluid (the mass flow of m 3) after entering the second auxiliary section 220, and mix with the cooling fluid after entering the heat exchange device 30, and then flow into the heat exchange structure 20 through the second auxiliary heat exchanger.

In addition, the opening degrees of the second port 520 and the third port 530 of the first multi-way valve 500 are used to control the mass flow rate of the coolant flowing into the first sub-section 120 to be m3-m2, thereby ensuring that the mass flow rate of the low-temperature coolant flowing into the first main section 110a is m3-m2, so that when the high-temperature coolant having the mass flow rate of m2 in the second circulation loop 201 flows into the first main section 110a, the mass flow rate of the coolant flowing into the first heat exchanger 30 can be ensured to be m3. At the same time, the mass flow rate of the cooling liquid entering the second main section 210b is ensured to be m2, so that after the part of cooling liquid is mixed with the high-temperature cooling liquid with the mass flow rate of m1-m2 flowing out of the second auxiliary section 220, the cooling liquid with the mass flow rate of m1 can be ensured to enter the second heat exchanger 40, namely, the mass flow rate of the cooling liquid entering the second heat exchanger 40 is ensured to be m1.

Referring to fig. 5 and 9, when the structure to be temperature-regulated 20 is independently heated or cooled, the second operation mode of the thermal management system may be adopted, that is, the first port 510 of the first multi-way valve 500 is controlled to be closed, the second port 520 and the third port 530 are connected, so that the cooling liquid in the second pipeline 200 flows in the second pipeline 200 and the second heat exchanger 40 in a circulating manner, that is, the cooling liquid circulates in the second circulation circuit 201, and the temperature of the cooling liquid in the second circulation circuit 201 is continuously controlled by the temperature control component 211, so that the mass flow rate and the temperature of the cooling liquid at the inlet end of the second heat exchanger 40 reach the target requirements, and therefore, when the cooling liquid enters the second heat exchanger 40, the cooling liquid can be subjected to heat exchange with the structure to be temperature-regulated 20, so that the temperature of the structure to be temperature-regulated 20 is controlled within the third target range.

Referring to FIG. 5, a first example is illustrated when a thermal management system receives a system demand: when the fourth target temperature at the inlet end of the second heat exchanger 40 is T1 and the mass flow rate is m1, the second operation mode of the thermal management system may be adopted, that is, the first port 510 of the first multi-way valve 500 is controlled to be closed, and the second port 520 and the third port 530 are controlled to be conducted, so that the cooling liquid in the second pipeline 200 independently circulates in the second circulation loop 201, and the mass flow rate of the cooling liquid at the inlet end of the second heat exchanger 40 is ensured to reach m1.

When the inlet end temperature Tn of the second heat exchanger 40 is less than T1, the cooling liquid in the second pipeline 200 may be heated by the temperature control component 211, so that tn=t1, and thus, when the cooling liquid enters the second heat exchanger 40, heat exchange with the structure to be tempered 20 may occur, so that the temperature of the structure to be tempered 20 is controlled within the third target temperature range.

When the inlet end temperature Tn > T1 of the second heat exchanger 40, the temperature of the cooling liquid in the second pipeline 200 can be reduced by the temperature control component 211, so that tn=t1, and when the cooling liquid enters the second heat exchanger 40, heat exchange with the structure 20 to be tempered can occur, so that the temperature of the structure 20 to be tempered is controlled within the third target range.

Referring to fig. 6 and 10, when the device 10 to be cooled is independently heated or cooled, a third operation mode of the thermal management system may be adopted, that is, the first port 510 and the third port 530 of the first multi-way valve 500 are controlled to be turned on, the second port 520 is closed, so that the cooling liquid circulates in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b and the second heat exchanger 40, and the temperature of the cooling liquid may be controlled by the temperature control component 211 on the second main section 210b, so that the temperature of the cooling liquid entering the inlet end of the first heat exchanger 30 may reach the second target temperature, and thus, when the cooling liquid enters the first heat exchanger 30, heat exchange with the device 10 to be cooled may occur, so that the temperature of the device 10 to be cooled is controlled within the first target temperature range.

Referring to FIG. 6, a first example is illustrated when a thermal management system receives a system demand: when the fourth target temperature at the inlet end of the first heat exchanger 30 is T2 and the mass flow rate is m3, the third operation mode of the thermal management system may be adopted, that is, the first port 510 and the third port 530 of the first multi-way valve 500 are controlled to be turned on, and the second port 520 is controlled to be turned off, so that the cooling liquid circulates in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b and the second heat exchanger 40, and the mass flow rate of the cooling liquid at the inlet end of the first heat exchanger 30 is ensured to reach m3.

When the inlet end temperature Tb of the first heat exchanger 30 is less than T2, the cooling liquid in the third circulation loop 301 may be heated by the temperature control assembly 211 such that tb=t2, so that heat exchange with the device 10 to be cooled may occur when the cooling liquid enters into the first heat exchanger 30, such that the temperature of the device 10 to be cooled is controlled within the first target temperature range.

When the inlet end temperature Tb of the second heat exchanger 40 is greater than T2, the temperature of the cooling liquid in the third circulation loop 301 may be reduced by the temperature control assembly 211 such that tb=t2, so that when the cooling liquid enters the first heat exchanger 30, heat exchange with the device 10 to be cooled may occur, so that the temperature of the device 10 to be cooled is controlled within the first target temperature range.

In this embodiment, the first multi-way valve 500 may be a proportional three-way valve, so as to simplify the control procedure of the first multi-way valve 500 and save the cost of the first multi-way valve 500. In addition, by setting the first multi-way valve 500 as a proportional three-way valve, the opening degrees of the three interfaces of the proportional three-way valve can be adjusted according to actual needs to adjust the mass flow rate of the cooling liquid entering the second circulation loop 201 from the first circulation loop 101, that is, adjust the mixing water proportion in the second circulation loop 201, so as to accurately control the temperature of the cooling liquid entering the first heat exchanger 30, and adjust the device to be cooled 10 to the target temperature.

Of course, in other examples, the first multi-way valve 500 may also be a proportional multi-way valve having at least three ports, such as a four-way valve or a five-way valve.

Fig. 11 is a schematic diagram of a first state in which a first operation mode of the thermal management system corresponding to fig. 1 is a heating mode, fig. 12 is a schematic diagram of a second state in which the first operation mode of the thermal management system corresponding to fig. 1 is a heating mode, fig. 13 is a schematic diagram of a second operation mode of the thermal management system corresponding to fig. 1 is a heating mode, and fig. 14 is a schematic diagram of a third operation mode of the thermal management system corresponding to fig. 1 is a heating mode. Referring to fig. 11 to 14, for example, when the operation mode of the thermal management system is a heating mode, i.e., the thermal management system heats the device to be cooled 10 (e.g., a battery) or the structure to be tempered 20 (e.g., a passenger compartment), the second heat exchanger 40 may be a warm air core 40a, and the temperature control assembly 211 may include, but is not limited to, at least one of a condensing plate heat exchanger 211a (abbreviated as condensing plate exchange in the drawing) and an electric heating core 221a to improve the heating efficiency of the cooling liquid. The temperature control assembly 211 may include a condensation plate heat exchanger 211a and an electric heating core 221a, where the electric heating core 221a is located between an outlet end of the condensation plate heat exchanger 211a and an inlet end of the warm air core 40a, so that, on one hand, the cooling liquid flows into the condensation plate heat exchanger 211a, the refrigerant in the condensation plate heat exchanger 211a emits heat during condensation and transfers the heat into the cooling liquid, so as to heat the cooling liquid, so that the temperature of the cooling liquid rises, the warmed cooling liquid continuously flows into the electric heating core 221a, and the cooling liquid is continuously heated by the electric heating core 221a, so that the temperature of the cooling liquid when reaching the inlet end of the second heat exchanger 40 can reach a fourth target temperature, on the one hand, the cooling liquid entering the second heat exchanger 40 can be guaranteed to raise the temperature in the structure 20 to be tempered to a third target temperature, and on the other hand, the heat exchange efficiency of the cooling liquid due to the fact that the temperature of the cooling liquid reaching the condensation plate heat exchanger 211a is too high is avoided.

In some examples, the cold plate heat exchanger 211a may include a cold plate heat exchange core for circulating a refrigerant (e.g., a refrigerant) and cold plate channels for circulating a cooling fluid such as water, and cold plate channels may surround the outer periphery of the cold plate heat exchange core, such that heat evolved during condensation of the refrigerant may be transferred to the cooling fluid within the cold plate channels through the side walls of the cold plate heat exchange core to increase the temperature of the cooling fluid. When configured, the condensing plate channel of the condensing plate heat exchanger 211a is connected in series with the second pipeline 200, for example, the inlet end of the warm air core 40a is communicated with the outlet end of the condensing plate channel, and the inlet end of the condensing plate channel can be communicated with the second end of the second main section 210 b.

The working principles of the condensation plate heat exchanger 211a and the electric heating core 221a according to the embodiments of the present application may refer to the content of county in the prior art, and will not be described herein.

In the following, three operation modes of the thermal management system will be described by taking the structure to be tempered 20 as a passenger cabin, the device to be cooled 10 as a battery, and the first heat exchanger 30 as a battery cooling plate as an example.

Referring to fig. 11, when the passenger compartment and the battery in the battery pack need to be simultaneously heated, for example, in winter, the first operation mode of the thermal management system may be operated to control the temperature and the mass flow rate of the coolant in the first circulation loop 101 to control the temperature of the coolant entering the inlet end of the warm air core 40a to reach the fourth target temperature, so that the coolant at the temperature can exchange heat with the air in the passenger compartment in the warm air core 40a to raise the temperature in the passenger compartment to reach the third target temperature.

In addition, when the temperature of the cooling liquid at the inlet end of the battery pack cooling plate is insufficient, the opening degree of the three interfaces of the first multi-way valve 500 can be adjusted to control the mass flow rate m2 (i.e. the reference mass flow rate m 2) of the cooling liquid exchanged between the second pipeline 200 and the first pipeline 100, so as to achieve the effect of adjusting the mixing ratio, i.e. the ratio of m2 in the mass flow rate m3 of the cooling liquid in the first pipeline 100 is controlled to increase the temperature of the cooling liquid in the first pipeline 100, and the temperature entering the inlet end of the battery pack cooling plate can be adjusted to reach the second target temperature.

Specifically, when the thermal management system receives a system demand: when the fourth target temperature at the inlet end of the warm air core 40a is T1, the mass flow rate is m1, the second target temperature at the inlet end of the battery pack cooling plate is T2, and the mass flow rate is m3, the cooling liquid in the first circulation loop 101 and the second circulation loop 201 can be controlled to circulate in the respective circulation loops, so as to achieve the target mass flow rate of the warm air core 40a as m1, and the target mass flow rate of the battery pack cooling plate as m3.

Referring to fig. 11, when the temperature Tn of the inlet end of the warm air core 40a is < T1, the cooling liquid in the second pipe 200 may be heated by the electric heating core 221a or the condensing plate heat exchanger 211a such that the temperature Tn of the inlet end of the warm air core 40a reaches the fourth target temperature T1, i.e., tn=t1.

Referring to fig. 11, when the temperature tb=t2 at the inlet end of the battery pack cooling plate, the first interface 510 of the first multi-way valve 500 may be controlled to be closed, the second interface 520 and the third interface 530 may be both turned on, i.e., the thermal management system is in the first state of the first operation mode, and the cooling liquid in the first circulation loop 101 and the second circulation loop 102 circulate in the respective circulation loops, i.e., the cooling liquid in the first circulation loop 101 may control the temperature of the battery within the first target temperature range through the battery pack cooling plate after entering the battery pack cooling plate.

Referring to fig. 12, when the temperature Tb at the inlet end of the battery pack cold plate is less than T2, all three interfaces of the first multi-way valve 500 are turned on to increase the ratio of the reference mass flow rate m2 to the mass flow rate m3, thereby increasing the temperature Tb to the final second target temperature T2.

Referring to fig. 13, when the passenger cabin is independently heated, the second operation mode of the thermal management system may be adopted, that is, the first port 510 of the first multi-way valve 500 is controlled to be closed, the second port 520 and the third port 530 are controlled to be conducted, so that the cooling liquid in the second circulation loop 201 independently circulates in the second circulation loop 201, the temperature of the cooling liquid is continuously controlled through the condensation plate heat exchanger 211a or the electric heating core 221a and the like, and the mass flow rate and the temperature of the cooling liquid at the inlet end of the warm air core 40a are ensured to reach the target requirements, so that heat exchange with the passenger cabin can be performed when the cooling liquid enters the warm air core 40a, and the temperature of the passenger cabin is controlled within the third target temperature range.

Referring to FIG. 13, specifically, when a thermal management system receives a system demand: when the fourth target temperature at the inlet end of the warm air core 40a is T1 and the mass flow rate is m1, the second working mode of the thermal management system may be adopted, that is, the first port 510 of the first multi-way valve 500 is controlled to be closed, and the second port 520 and the third port 530 are controlled to be conducted, so that the cooling liquid in the second pipeline 200 independently circulates in the second pipeline 200, and the mass flow rate of the cooling liquid at the inlet end of the warm air core 40a is ensured to reach m1.

When the inlet end temperature Tn < T1 of the warm air core 40a, the cooling liquid in the second pipe 200 may be heated by the condensation plate heat exchanger 211a or the like such that tn=t1, so that heat exchange with the passenger compartment may occur when the cooling liquid enters into the warm air core 40a such that the temperature of the passenger compartment is controlled within the third target temperature range.

Referring to fig. 14, when the battery is independently heated, a third operation mode of the thermal management system may be adopted, that is, the first port 510 and the third port 530 of the first multi-way valve 500 are controlled to be turned on, the second port 520 is closed, so that the cooling liquid circulates in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b and the warm air core 40a, the temperature of the cooling liquid is controlled by the condensation plate heat exchanger 211a or the electric heating core 221a of the second main section 210b, so that the temperature of the cooling liquid entering the inlet end of the battery pack cooling plate can reach the second target temperature, and heat exchange with the battery can occur when the cooling liquid enters the battery pack cooling plate, so that the temperature of the battery is controlled within the first target range.

Referring to FIG. 14, specifically, when a thermal management system receives a system demand: when the second target temperature at the inlet end of the battery pack cold plate is T2 and the mass flow rate is m3, the third working mode of the thermal management system may be adopted, that is, the first interface 510 and the third interface 530 of the first multi-way valve 500 are controlled to be turned on, and the second interface 520 is controlled to be turned off, so that the cooling liquid circulates in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b and the warm air core 40a, and the mass flow rate of the cooling liquid at the inlet end of the battery pack cold plate is ensured to reach m3.

When the inlet end temperature Tb of the battery pack cooling plate is less than T2, the cooling liquid in the above-described circulation loop may be heated by the condensation plate heat exchanger 211a or the like such that tb=t2, so that heat exchange with the battery may occur when the cooling liquid enters into the battery pack cooling plate such that the temperature of the battery is controlled within the first target range.

In the third operation mode, the warm air core 40a is only used as a pipe, that is, the warm air core 40a does not exchange heat between the coolant and the passenger compartment.

In some examples, when the passenger compartment is heated, the target temperature of the cooling fluid at the inlet end of the warm air core 40a (i.e., the fourth target temperature T1) is 40-80 ℃, i.e., the cooling fluid in the second circulation loop 201, such as the second pipeline 200, can be heated by the condensing plate heat exchanger 211a or the electric heating core 221a to provide the cooling fluid temperature of 40-80 ℃ to the warm air core 40a, ensuring that the passenger compartment temperature reaches the third target temperature between 40-80 ℃.

When the battery heats, the target temperature of the cooling liquid at the inlet end of the battery pack cooling plate (i.e. the second target temperature T2) is 0-40 ℃, for example, the first working mode of the thermal management system can be adopted, part of the cooling liquid in the second circulation loop 201 is mixed with the cooling liquid in the first circulation loop 101 to increase the temperature of the cooling liquid in the first circulation loop 101, or the third working mode of the thermal management system is adopted, the cooling liquid in the third circulation loop 301 is heated by the condensing plate heat exchanger 211a or the electric heating core 221a to increase the temperature of the cooling liquid in the third circulation loop 301, so that the cooling liquid temperature of 0-40 ℃ is provided for the battery pack cooling plate, and the temperature of the battery is ensured to reach the third target temperature between 0-40 ℃.

In winter, when the passenger compartment and the battery are simultaneously heated, the third target temperature of the passenger compartment is greater than the first target temperature of the battery. For example, when the third target temperature of the passenger cabin is 60 ℃ to 80 ℃, the first target temperature of the battery is 20 ℃ to 40 ℃, and when the passenger cabin and the battery in the battery pack are simultaneously heated, the fourth target temperature of the cooling liquid at the inlet end of the warm air core 40a is 60 ℃ to 80 ℃, and the second target temperature of the cooling liquid at the inlet end of the battery cooling plate is 20 ℃ to 40 ℃, the temperature of the cooling liquid in the second circulation loop 201 is greater than the temperature of the cooling liquid in the first circulation loop 101, so that when the temperature of the cooling liquid at the inlet end of the battery cooling plate is insufficient, the first working mode of the thermal management system can be adopted, namely, by adjusting the opening degree of the three interfaces of the first multi-way valve 500, part of the high-temperature cooling liquid in the second circulation loop 201 can flow into the first circulation loop 101 to raise the temperature of the cooling liquid in the first circulation loop 101, and the temperature of the cooling liquid at the inlet end of the battery cooling plate reaches the second target temperature, so that the temperature of the battery is ensured to be in the first target range.

Fig. 15 is a schematic diagram of a first state in which a first operation mode of the thermal management system corresponding to fig. 1 is a cooling mode, fig. 16 is a schematic diagram of a second state in which the first operation mode of the thermal management system corresponding to fig. 1 is a cooling mode, fig. 17 is a schematic diagram of a second operation mode of the thermal management system corresponding to fig. 1 is a cooling mode, and fig. 18 is a schematic diagram of a third operation mode of the thermal management system corresponding to fig. 1 is a cooling mode. Referring to fig. 15 to 18, continuing with the first example, when the operation mode of the thermal management system is a cooling mode, i.e., the thermal management system cools the device to be cooled 10 (e.g., a battery) or the structure to be tempered 20 (e.g., a passenger compartment), the second heat exchanger 40 may be a cold air core 40b, and the temperature control assembly 211 may include, but is not limited to, an evaporating plate heat exchanger 211b (abbreviated as evaporating plate exchange in the drawing) or the like, to improve the cooling efficiency of the cooling liquid.

Illustratively, the evaporating plate heat exchanger 211b may be connected in series between the second end of the second main section 210b and the inlet end of the second heat exchanger 40 (the cold air core 40 b), such that the cooling fluid flows into the evaporating plate heat exchanger 211b, and the refrigerant in the evaporating plate heat exchanger 211b absorbs heat during evaporation, i.e., absorbs the cooling fluid to obtain heat, so that the temperature of the cooling fluid is reduced, such that the temperature of the cooled cooling fluid reaches the inlet end of the cold air core 40b to reach the fourth target temperature, and it may be ensured that the cooling fluid entering the cold air core 40b can raise the temperature of the structure 20 (e.g., the passenger compartment) to be tempered to the third target temperature.

In some examples, the evaporator plate heat exchanger 211b may include an evaporator plate heat exchanger core for circulating a refrigerant and an evaporator plate passage for circulating a cooling fluid, such as water, around the periphery of the evaporator plate heat exchanger core such that the refrigerant evaporates by absorbing heat from the cooling fluid in the evaporator plate passage through the side walls of the evaporator plate heat exchanger core to reduce the temperature of the cooling fluid. When disposed, the evaporator plate passages of the evaporator plate heat exchanger 211b are connected in series with the second conduit 200, e.g., the inlet end of the cold air core 40b is in communication with the outlet end of the evaporator plate passages, which may be in communication with the second end of the second main section 210 b. The working principle of the evaporating plate heat exchanger 211b in the embodiment of the present application may refer to the related content of the prior art, and will not be described herein.

In summer, for example, when the passenger compartment and the battery are cooled, the third target temperature of the passenger compartment is less than the first target temperature of the battery body. For example, when the third target temperature of the passenger cabin is 0 ℃ to 8 ℃, the first target temperature of the battery is 15 ℃ to 20 ℃, and when the passenger cabin and the battery in the battery pack are simultaneously cooled, the fourth target temperature of the cooling liquid at the inlet end of the cold air core 40b is 0 ℃ to 8 ℃, the second target temperature of the cooling liquid at the inlet end of the battery pack cooling plate is 15 ℃ to 20 ℃, and the temperature of the cooling liquid in the second circulation loop 201 is smaller than the temperature of the cooling liquid in the first circulation loop 101, so that when the temperature of the cooling liquid at the inlet end of the battery pack cooling plate is too high, the first working mode of the thermal management system can be adopted, namely, the opening degree of the three interfaces of the first multi-way valve 500 is adjusted to be larger than zero, so that part of the low-temperature cooling liquid in the second circulation loop 201 can flow into the first circulation loop 101 to reduce the temperature of the cooling liquid in the first circulation loop 101, so that the temperature of the cooling liquid at the inlet end of the battery pack cooling plate reaches the second target temperature, and the temperature of the battery is ensured to be in the first target range.

Referring to fig. 15, specifically, in summer, the passenger compartment and the battery in the battery pack are both subjected to refrigeration, and the first operation mode of the thermal management system may be adopted to control the temperature and the mass flow rate of the cooling liquid in the second circulation loop 201 so as to control the temperature of the cooling liquid entering the inlet end of the cold air core 40b to reach the fourth target temperature, so that the cooling liquid at the temperature can exchange heat with the air in the passenger compartment in the cold air core 40b, thereby reducing the temperature in the passenger compartment and enabling the temperature in the passenger compartment to reach the third target temperature.

When the temperature of the cooling liquid at the inlet end of the battery pack cooling plate is too high, the opening degree of the three interfaces of the first multi-way valve 500 can be adjusted to control the mass flow m2 (i.e. the reference mass flow m 2) of the cooling liquid exchanged between the second circulation loop 201 and the first circulation loop 101, so as to realize the effect of adjusting the mixing ratio, i.e. the duty ratio of m2 in the mass flow m3 of the cooling liquid in the first circulation loop 101 is controlled to reduce the temperature of the cooling liquid in the first circulation loop 101, and the temperature entering the inlet end of the battery pack cooling plate can be adjusted to reach the second target temperature.

Specifically, when the thermal management system receives a system demand: when the fourth target temperature at the inlet end of the cold air core 40b is T1, the mass flow rate is m1, the second target temperature at the inlet end of the battery pack cold plate is T2, and the mass flow rate is m3, the cooling liquid in the second circulation loop 201 and the cooling liquid in the first circulation loop 101 can be controlled to circulate in the respective circulation loops, so as to achieve the target mass flow rate of the cold air core 40b is m1, and the target mass flow rate of the battery pack cold plate is m3.

Referring to fig. 15, when the temperature Tn > T1 of the inlet end of the cool air core 40b, the cooling liquid in the second circulation loop 201 may be cooled by the evaporating plate heat exchanger 211b such that the temperature Tn of the inlet end of the cool air core 40b is reduced to a fourth target temperature T1, i.e., tn=t1.

Referring to fig. 15, when the temperature tb=t2 at the inlet end of the battery pack cooling plate, the first interface 510 of the first multi-way valve 500 may be controlled to be closed, the second interface 520 and the third interface 530 may be both turned on, i.e., the thermal management system is in the first state of the first operation mode, and the cooling liquid in the first circulation loop 101 and the second circulation loop 102 circulate in the respective circulation loops, i.e., the cooling liquid in the first circulation loop 101 may control the temperature of the battery within the first target temperature range through the battery pack cooling plate after entering the battery pack cooling plate.

Referring to fig. 16, when the temperature Tb of the inlet end of the battery pack cold plate is greater than T2, all three ports of the first multi-way valve 500 are turned on to increase the mass flow rate of the first port 510, decrease the opening degree of the second port 520 to decrease the mass flow rate of the second port 520 to increase the ratio of the reference mass flow rate m2 to the mass flow rate m3, thereby lowering the temperature Tb to the final second target temperature T2.

Referring to fig. 17, when the passenger cabin is independently cooled, the second operation mode of the thermal management system may be adopted, that is, the first port 510 of the first multi-way valve 500 is controlled to be closed, the second port 520 and the third port 530 are connected, so that the cooling liquid in the second circulation loop 201 independently circulates in the second circulation loop 201, the temperature of the cooling liquid is continuously controlled by the evaporating plate heat exchanger 211b, and the mass flow rate and the temperature of the cooling liquid at the inlet end of the cold air core 40b are ensured to reach the target requirements, so that when the cooling liquid enters the cold air core 40b, heat exchange with the passenger cabin may occur, and the temperature of the passenger cabin is controlled within the third target range.

Specifically, when the thermal management system receives a system demand: when the fourth target temperature at the inlet end of the cold air core 40b is T1 and the mass flow rate is m1, the second operation mode of the thermal management system may be adopted, that is, the first interface 510 of the first multi-way valve 500 is controlled to be closed, and the second interface 520 and the third interface 530 are controlled to be conducted, so that the cooling liquid in the second circulation loop 201 independently circulates in the second circulation loop 201, and the mass flow rate of the cooling liquid at the inlet end of the cold air core 40b is ensured to reach m1.

When the inlet end temperature Tn > T1 of the cool air core 40b, the cooling liquid in the second pipeline 200 may be heated by the evaporating plate heat exchanger 211b such that tn=t1, so that heat exchange with the passenger compartment may occur when the cooling liquid enters into the cool air core 40b, such that the temperature of the passenger compartment is controlled within the third target range.

Referring to fig. 18, when the batteries in the battery pack are individually cooled, a third operation mode of the thermal management system may be adopted, that is, the first port 510 and the third port 530 of the first multi-way valve 500 are controlled to be turned on, the second port 520 is closed, so that the cooling liquid circulates in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b and the cold air core 40b, and the temperature of the cooling liquid is controlled by the evaporating plate heat exchanger 211b on the second main section 210b, so that the temperature of the cooling liquid entering the inlet end of the cooling plate of the battery pack can reach the second target temperature, and thus, when the cooling liquid enters the cooling plate of the battery pack, heat exchange with the batteries can occur, so that the temperature of the batteries is controlled within the first target range.

Referring to FIG. 18, specifically, when a thermal management system receives a system demand: when the second target temperature at the inlet end of the battery pack cold plate is T2 and the mass flow rate is m3, the third working mode of the thermal management system may be adopted, that is, the first interface 510 and the third interface 530 of the first multi-way valve 500 are controlled to be turned on, and the second interface 520 is controlled to be turned off, so that the cooling liquid circulates in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b and the cold air core 40b, thereby ensuring that the mass flow rate of the cooling liquid at the inlet end of the battery pack cold plate reaches m3.

When the temperature Tb of the inlet end of the battery pack cooling plate is greater than T2, the cooling liquid in the circulation loop may be cooled by the evaporation plate heat exchanger 211b such that tb=t2, and thus, when the cooling liquid enters the battery pack cooling plate, heat exchange with the battery may occur, so that the temperature of the battery is controlled within the first target range.

In the third operation mode, the cold air core 40b is only used as a pipe, that is, the cold air core 40b does not exchange heat between the coolant and the passenger compartment.

In this embodiment, the second pipeline 200 and the first pipeline 100 are disposed in the thermal management system, and the first pipeline 100 is connected in parallel to the second pipeline 200 through the first pipe section 300 and the second pipe section 400, and in addition, the first multi-way valve 500 is disposed on the inlet end of the first pipe section 300 and the second pipeline 200, or the first multi-way valve 500 is disposed on the inlet end of the second pipe section 400 and the first pipeline 100, so that the second pipeline 200 and the first pipeline 100 in the thermal management system can be operated simultaneously by opening and adjusting the opening of each interface in the first multi-way valve 500. When the second pipeline 200 and the first pipeline 100 are simultaneously heated (i.e. when the device to be cooled 10 and the structure to be tempered 20 are simultaneously heated), and the temperature of the cooling liquid in the second pipeline 200 is higher than the temperature of the cooling liquid in the first pipeline 100, the openings of the first port 510, the second port 520 and the third port 530 of the first multi-way valve 500 can be opened and adjusted, so that part of the cooling liquid in the second pipeline 200 enters the first pipeline 100 through the first pipeline section 300 to increase the mass flow rate and the temperature of the cooling liquid in the first pipeline 100, thereby increasing the temperature of the inlet end of the first heat exchanger 30, so that the first heat exchanger 30 cools the device to be cooled 10 (for example, a battery) to a proper range, and in addition, part of the cooling liquid passing through the first heat exchanger 30 can enter the second pipeline 200 through the second pipeline section 400, so that the mass flow rate and the temperature entering the second heat exchanger 40 in a proper range are ensured, so that the second heat exchanger 40 adjusts the temperature of the structure to be tempered 20 (for example, a cabin) to a proper range, thereby playing a role in balancing the effect of cooling the device to be cooled 10 and the temperature of the structure to be tempered 20.

In addition, the heat management system of the embodiment of the application is simple in structure, simple and convenient in control method and low in cost.

By providing the temperature control assembly 211 in the second pipeline 200, the temperature of the cooling liquid in the second pipeline 200 can be adjusted by the temperature control assembly 211 to ensure that the temperature of the inlet end of the second heat exchanger 40 reaches a proper range, so when the device 10 to be cooled and the structure 20 to be tempered work (such as heating) simultaneously, i.e. the first heat exchanger 30 and the second heat exchanger 40 of the thermal management system work (such as heating) simultaneously, the temperature of the cooling liquid in the second circulation loop 201 can be raised to the target temperature by the temperature control assembly 211 first, and then the opening of the three interfaces of the first multi-way valve 500 is adjusted to be greater than zero, so that part of the cooling liquid in the second circulation loop 201 enters the first circulation loop 101 to raise the temperature and the mass flow of the cooling liquid entering the first heat exchanger 30 in the first circulation loop 101, so that the temperature of the inlet end of the first heat exchanger 30 reaches the target temperature.

In addition, when the device 10 to be cooled independently works (e.g. heats), the opening degrees of the three interfaces of the first multi-way valve 500 can be adjusted, for example, the opening degrees of the first interface 510 and the third interface 530 can be adjusted to be greater than zero, and the opening degree of the second interface 520 is equal to zero, so that the cooling liquid flowing out from the outlet end of the first heat exchanger 30 can enter the temperature control assembly 211 in the second main section 210b through the second pipe section 400, after the temperature control assembly 211 heats the cooling liquid, the cooling liquid can flow out from the outlet end of the temperature control assembly 211, and enter the first main section 110a of the first pipeline 100 through the second main section 210a and the first pipe section 300, and finally enter the first heat exchanger 30, so that the high-temperature cooling liquid entering the first heat exchanger 30 exchanges heat with the device 10 to be cooled (e.g. a battery).

Referring to fig. 18, in some examples, the second pipeline 200 has a first water pump 212 thereon, and an outlet end of the first water pump 212 may be in communication with an inlet end of the temperature control assembly 211, i.e., an outlet end of the first water pump 212 is in communication with an inlet end of the second heat exchanger 40. For example, the first water pump 212 may be connected in series with the second secondary section 220, the second primary section 210a, or the second primary section 210 b.

By arranging the first water pump 212 on the second pipeline 200, the mass flow rate of the cooling liquid on the second main section 210 can be regulated by regulating the rotation speed of the first water pump 212, so as to precisely control the mass flow rate of the cooling liquid entering the second heat exchanger 40, ensure that the cooling liquid at the inlet end of the second heat exchanger 40 is within the fourth target temperature, and ensure that the temperature of the structure to be regulated 20 reaches the third target temperature.

In some embodiments, the first water pump 212 may be connected in series between the outlet end of the second pipe section 400 and the temperature control component 211, for example, the inlet end of the first water pump 212 is connected in communication with the outlet end of the second pipe section 400, and the outlet end of the first water pump 212 is connected in series with the temperature control component 211, that is, the first water pump 212 is connected in series to the second main section 210b, so that when the thermal management system is in the first working mode and the third working mode, the power of the cooling liquid entering the temperature control component 211 from the outlet end of the first heat exchanger 30 through the second pipe section 400 can be improved, that is, the reliability of the cooling liquid entering the second pipe section 200 of the first pipe 100 is improved, and when the device to be cooled 10 heats alone (or cools alone) (as shown in fig. 18) or the device to be cooled 10 and the structure to be cooled 20 heat simultaneously (or refrigerates simultaneously) (as shown in fig. 16), part or all of the cooling liquid flowing out from the outlet end of the first heat exchanger 30 can enter the second main section 210b of the second pipe section 200 well.

Referring to fig. 18, in addition, in some examples, the first pipeline 100 may have a second water pump 111, where the second water pump 111 is connected in series to the first main section 110, for example, the second water pump 111 may be connected in series to the first main section 110a or the first main section 110b, so that, on one hand, the second water pump 111 may provide kinetic energy to the cooling liquid in the first pipeline 100 to ensure stable flow of the cooling liquid in the first pipeline 100, and on the other hand, by adjusting the rotation speed of the second water pump 111, the mass flow rate of the cooling liquid on the first main section 110 in the first pipeline 100 may be controlled, thereby playing a role in controlling the mass flow rate and the temperature of the cooling liquid at the inlet end of the first heat exchanger 30.

In some examples, the inlet end of the second water pump 111 is in communication with the outlet end of the first pipe section 300, and the outlet end of the second water pump 111 is in communication with the inlet end of the first heat exchanger 30, i.e. the second water pump 111 is connected in series with the first main section 110a, so that when the thermal management system is in the first or third operation mode, the power of the cooling liquid entering the first pipe 100 from the second pipe 200 through the first pipe section 300 can be increased, and it is ensured that part or all of the cooling liquid in the second pipe 200 can well enter the first pipe 100.

With continued reference to fig. 1 and 2, in some examples, the thermal management system may further include an on-off valve 600.

When the thermal management system is of a first example configuration (shown with reference to fig. 1), i.e., the first multi-way valve 500 is connected in series with the first pipeline 100, the on-off valve 600 is located on the second sub-section 220 of the second pipeline 200, and the inlet end of the on-off valve 600 is in communication with the inlet end b1 of the second sub-section 220, and the outlet end of the on-off valve 600 is in communication with the outlet end a1 of the second sub-section 220.

Referring to fig. 3 to 5, the on-off valve 600 is turned on in the first operation mode and the second operation mode of the thermal management system to conduct the second pipeline 200 and form the second circulation loop 201, so that the temperature of the structure 20 to be regulated can be regulated after the cooling liquid in the second circulation loop 201 enters the second heat exchanger 40.

Referring to fig. 6, the on-off valve is used to be turned off in the third operation mode, so that the first heat exchanger 30, the two first main sections 110, the second pipe section 400, the second heat exchanger 40, the two second main sections 210 and the first pipe section 300 form a third circulation loop 301, for example, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b, the second heat exchanger 40, the second main section 210a, the first pipe section 300 and the first main section 110a are sequentially connected in series to form the third circulation loop 301, so that the cooling liquid in the third circulation loop 301 can reach the second target temperature under the adjustment of the temperature control component 211 on the second main section 210, and the temperature of the liquid cooling device 10 can be adjusted to the first target temperature after the cooling liquid enters the first heat exchanger 30.

Referring to fig. 6, for example, when the thermal management system is in the third working mode, i.e. when the liquid cooling device 10 is to be independently heated or cooled (e.g. heated), the opening/closing valve 600 and the port (i.e. the second port 520) of the first multiway valve 500, which is in communication with the first auxiliary section 120, are closed, and the port (510) of the first multiway valve 500 and the port (520) of the outlet end of the first main section 110 are opened, so that the cooling liquid enters the temperature control assembly 211 of the second pipeline 200 through the first main section 110b and the second pipe section 400 to be heated, and then enters the first auxiliary section 110a of the first pipeline 100 through the second main section 210a and the first pipe section 300, and enters the first heat exchanger 30, so as to raise the temperature of the cooling liquid entering the first heat exchanger 30, thereby raising the temperature of the liquid cooling device 10 to a proper range, and avoiding that the cooling liquid flowing out through the outlet end of the first heat exchanger 30 enters the second pipe section 400 directly into the second section 220, and then enters the second auxiliary section 220 from the second pipe section 300 and the first pipe section 300 to the second auxiliary section 110a directly into the second auxiliary section 110a of the second pipeline 200, and the short circuit is avoided at the inlet end 301 of the second pipeline 200.

Referring to fig. 2, when the thermal management system is of a second example structure, i.e., the first multi-way valve 500 is connected in series to the second pipe 200, the switching valve 600 is positioned on the first sub-section 120, and the inlet end of the switching valve 600 communicates with the inlet end of the first sub-section 120, and the outlet end of the switching valve 600 communicates with the outlet end of the first sub-section 120.

Referring to fig. 7 and 8, the on-off valve 600 is turned on in the first operation mode of the thermal management system to turn on the first pipe 100 and form the first circulation loop 101, so that the temperature of the temperature-adjusting device 11 can be adjusted after the cooling liquid in the first circulation loop 101 enters the first heat exchanger 30.

Referring to fig. 10, the on-off valve 600 is turned off in the third operation mode, so that the first heat exchanger 30, the two first main sections 110, the second pipe section 400, the second heat exchanger 40, the two second main sections 210 and the first pipe section 300 form a third circulation loop 301, for example, the first heat exchanger 30, the first main section 110b, the second pipe section 400, the second main section 210b, the second heat exchanger 40, the second main section 210a, the first pipe section 300 and the first main section 110a are sequentially connected in series to form the third circulation loop 301, so that the cooling liquid in the third circulation loop 301 can reach the second target temperature under the adjustment of the temperature control component 211 on the second main section 210, and the temperature of the device 10 to be cooled can be adjusted to the first target temperature after the cooling liquid enters the first heat exchanger 30.

For example, when the device 10 to be cooled is independently heated or cooled (e.g., independently heated), the port (i.e., the second port 520) of the first multi-way valve 500, which is connected to the second sub-section 220, may be closed, and the port (i.e., the third port 530) of the first multi-way valve 500, which is connected to the second main section 210a, is opened, so that the cooling liquid enters the temperature control assembly 211 of the second pipeline 200 through the first main section 110b and the second pipe section 400 to heat and raise the temperature, and the heated cooling liquid enters the first main section 110a of the first pipeline 100 through the second main section 210a and the first pipe section 300, and enters the first heat exchanger 30 to raise the temperature of the cooling liquid entering the first heat exchanger 30, thereby raising the temperature of the device 10 to be cooled to a suitable range, and avoiding that the cooling liquid flowing out through the outlet end of the first heat exchanger 30 enters the first sub-section 120 directly after passing through the first main section 110a, then enters the inlet end of the first heat exchanger 30 directly from the first main section 110a, and enters the second sub-section 200 after the second main section 200, and the short circuit is avoided in the second sub-section 200, which is not heated in the second main section 200, and enters the first heat exchanger 120.

Referring to fig. 11 and 12, for example, when the passenger compartment and the battery in the battery pack need to be simultaneously heated, for example, in winter, the first operation mode, that is, the warm air core 40a, the battery pack cooling plate, the electric heating core 221a, the cooling plate heat exchanger 211a, the first water pump 212, the second water pump 111, and the switching valve 600 are turned on, the cooling liquid in the second pipeline 200, that is, the second circulation circuit 201 is heated by the electric heating core 221a and the cooling plate heat exchanger 211a to control the temperature of the cooling liquid in the second circulation circuit 201, and the rotational speed of the first water pump 212 is adjusted to control the mass flow rate of the cooling liquid in the second circulation circuit 201 into the warm air core 40a, so that the temperature of the cooling liquid at the temperature reaches the fourth target temperature, and the cooling liquid at the temperature can exchange with the air in the passenger compartment in the warm air core 40a to increase the temperature in the passenger compartment to reach the third target temperature in the passenger compartment.

In addition, the mass flow rate of the cooling liquid entering the battery pack cooling plate in the first circulation circuit 101 is controlled by adjusting the rotation speed of the second water pump 111.

Referring to fig. 12, when the temperature of the cooling liquid at the inlet end of the battery pack cooling plate is insufficient, the opening degree of the three ports of the first multi-way valve 500 can be adjusted to control the mass flow rate m2 (i.e. the reference mass flow rate m 2) of the cooling liquid exchanged between the second circulation loop 201 and the first circulation loop 101, so as to achieve the effect of adjusting the mixing ratio, i.e. the ratio of m2 in the mass flow rate m3 of the cooling liquid in the first circulation loop 101 is controlled to raise the temperature of the cooling liquid in the first circulation loop 101, and the temperature entering the inlet end of the battery pack cooling plate can be adjusted to reach the second target temperature.

Referring to fig. 13, when the passenger compartment is independently heated, the second operation mode of the thermal management system may be adopted, that is, the first port 510 of the first multi-way valve 500 is controlled to be closed, the second port 520 and the third port 530 are turned on, the on-off valve 600 is opened, the second water pump 111 is closed, the cooling liquid in the second circulation loop 201 circulates independently in the second circulation loop 201, the temperature of the cooling liquid is continuously controlled by the condensing plate heat exchanger 211a or the electric heating core 221a, etc., the temperature of the cooling liquid at the inlet end of the warm air core 40a is ensured to reach the fourth target temperature, the rotational speed of the first water pump 212 is adjusted to ensure that the mass flow rate of the cooling liquid at the inlet end of the warm air core 40a reaches the target requirement, so that heat exchange with the passenger compartment can occur when the cooling liquid enters the warm air core 40a, and the temperature of the passenger compartment is controlled within the third target range.

Referring to fig. 14, when the batteries in the battery pack are independently heated, the third operation mode of the thermal management system may be adopted, that is, the first port 510 and the third port 530 of the first multi-way valve 500 are controlled to be turned on, the second port 520 is closed, the switch valve 600 is turned off, the first water pump 212 and the second water pump 111 are both turned on, so that the cooling liquid flows in the third circulation loop 301 formed by the second main section 210a, the first pipe section 300, the first main section 110a, the battery pack cold plate, the first main section 110b, the second pipe section 400, the second main section 210b and the warm air core 40a in a circulating manner, the cooling liquid temperature may be controlled by the condensation plate heat exchanger 211a or the electric heating core 221a on the second main section 210b, so that the cooling liquid temperature entering the inlet end of the battery pack cold plate can reach the second target temperature, and simultaneously, by adjusting the rotation speeds of the first water pump 212 and the second water pump 111, the mass flow of the cooling liquid entering the inlet end of the battery pack cold plate can reach the target requirements, so that the cooling liquid enters the battery pack cold plate and exchanges heat with the battery pack, and the battery pack cold plate can exchange heat with the battery in the first target temperature range.

The on-off valve 600 may be a check valve 600a or a stop valve 600b to simplify the control process of the on-off valve 600 and save the cost of the on-off valve 600.

Referring to fig. 14 and 18, taking the on-off valve 600 as the check valve 600a and being located on the second sub-section 220 as an example, when the first water pump 212 is located on the outlet side of the second sub-section 220, that is, the first water pump 212 is connected in series on the second main section 210b, and the second water pump 111 is located on the outlet side of the first sub-section 120, that is, the second water pump 111 is connected in series on the first main section 110a, for example, when the battery is in the third working mode, the rotation speed of the first water pump 212 and the second water pump 111 can be adjusted, so that when the to-be-cooled device 10 heats (or cools) independently, the rotation speed of the second water pump 111 is greater than the rotation speed of the first water pump 212, the pressure at the inlet end of the check valve 600a is smaller than the pressure at the outlet end, so that the check valve 600a can be reversely turned off, and the cooling liquid flowing out from the first main section 110b of the first pipeline 100 is prevented from being directly shorted at the second sub-section 220, and being unable to enter the second main section 210 of the second pipeline 200, for heating, for example, when the battery is in the third working mode, the battery heats independently, the battery heats up independently, so that the rotation speed of the second water pump 111 and the rotation speed of the first water pump 111 and the second water pump 212 can be adjusted to be completely cooled down at the temperature of the second water pump 210b, and the second water pump is completely flows into the second heat pump 210, or the cooling end at the inlet end of the second heat pump 210, thereby cooling end is completely at the temperature of the second pump is completely, and the second water pump is completely flows into the second heat pump 210, and is cooled down at the second pump is cooled, and has the temperature at the temperature, and has been cooled temperature.

Referring to fig. 1, it will be appreciated that in the above three operation modes, the pipe sections formed by the two second main sections and the second heat exchanger 40 each serve to control the temperature of the coolant in the corresponding mode, and thus, for convenience of description, the pipe sections formed by the two second main sections 210a (210 b) and the second heat exchanger 40 may be used as the temperature control pipe sections 2011.

As can be seen from the foregoing, when the thermal management system according to the embodiment of the present application is in the heating mode (see fig. 11 to 14), the second heat exchanger 40 in the temperature-controlled tube section 2011 is the warm air core 40a, the temperature-controlled component 211 is a heating component, for example, the temperature-controlled component 211 is at least one of the condensation plate heat exchanger 211a and the electric heating core 221a, that is, the temperature-controlled tube section 2011 formed by the two second main sections 210a (210 b) and the warm air core 40a is the heating tube section 201a.

When the thermal management system of the embodiment of the present application is in the cooling mode, the second heat exchanger 40 in the temperature control pipe section 2011 is the cold air core 40b, the temperature control component 211 is a cooling component, for example, the temperature control component 211 is the evaporation plate heat exchanger 211b, that is, the temperature control pipe section 2011 formed by the two second main sections 210a (210 b) and the cold air core 40b is the cooling pipe section 201b.

In some examples, when it is desired to adjust the thermal management system to a heating mode, for example, during winter, the second heat exchanger 40 may be replaced with a warm air core 40a, and the temperature control assembly 211 may be replaced with a heating assembly (e.g., a condensing plate heat exchanger 211 a) such that the temperature control tube segment 2011 is the heating tube segment 201a, thereby placing all three modes of operation of the thermal management system in the heating mode.

When the thermal management system needs to be adjusted to the cooling mode, for example, in summer, the second heat exchanger 40 may be replaced with the cold air core 40b, and the temperature control component 211 may be replaced with the cooling component (for example, the evaporating plate heat exchanger 211 b), so that the temperature control pipe segment 2011 is the cooling pipe segment 201b, so that all three working modes of the thermal management system are in the cooling mode.

FIG. 19 is a schematic diagram of yet another embodiment of a thermal management system according to the present application. Referring to fig. 19, in other examples, the number of the temperature-controlled pipe sections 2011 is two, and the two temperature-controlled pipe sections 2011 include a cooling pipe section 201b and a heating pipe section 201a, that is, one temperature-controlled pipe section 2011 is a cooling pipe section 201b, the other temperature-controlled pipe section 2011 is a heating pipe section 201a, and the cooling pipe section 201b and the heating pipe section 201a are disposed in parallel at two ends of the second sub-section 220.

It will be appreciated that the heating tube segment 201a includes two second main segments 210a and a second heat exchanger 40 communicating between the first end openings of the two second main segments 210a, and correspondingly, the cooling tube segment 201b includes two second main segments 210a and a second heat exchanger 40 communicating between the first end openings of the two second main segments 210 a. The second heat exchanger 40 of the heating pipe 201a is a warm air core 40a, and the temperature control component 211 of the heating pipe 201a is a heating component, for example, the temperature control component 211 of the heating pipe 201a may include at least one of a condensation plate heat exchanger 211a and an electric heating core 221a, so as to improve the heating efficiency of the cooling liquid. In addition, the second heat exchanger 40 of the cooling tube 201b is a cold air core 40b, and the temperature control component 211 of the cooling tube 201b is a cooling component, for example, the temperature control component 211 of the cooling tube 201b may include an evaporating plate heat exchanger 211b to improve cooling efficiency of the cooling liquid.

In particular, the thermal management system may include a second multi-way valve 700 through which the two ends of the cooling 201b and heating 201a tube segments communicate with the two ends of the second secondary segment 220, respectively. It should be noted that, the two ends of the cooling tube segment 201b refer to the second ends of the two second main segments 210 in the cooling tube segment 201b (i.e., the two ends facing away from the second heat exchanger 40), and correspondingly, the two ends of the heating tube segment 201a refer to the second ends of the two second main segments 210 in the heating tube segment 201a (i.e., the two ends facing away from the second heat exchanger 40).

Of the two second main sections 210, the second end of the second main section 210a is an outlet end, and the second end of the second main section 210b is an inlet end, that is, the inlet end of the temperature-controlled pipe section 2011, for example, the heating pipe section 201a (or the cooling pipe section 201 b) is the second end of the second main section 210b, and the outlet end of the temperature-controlled pipe section 2011, for example, the heating pipe section 201a (or the cooling pipe section 201 b) is the second end of the second main section 210 a.

Illustratively, the second multi-way valve 700 may include a fourth port 710, a fifth port 720, a sixth port 730, a seventh port 740, an eighth port 750, and a ninth port 760, with openings at both ends of the heating pipe segment 201a in communication with the fourth port 710 and the fifth port 720, respectively, e.g., an inlet end of the heating pipe segment 201a in communication with the fourth port 710 and an outlet end of the heating pipe segment 201a in communication with the fifth port 720.

Both ends of the refrigerating pipe section 201b are respectively communicated with the sixth interface 730 and the seventh interface 740, for example, an inlet end of the refrigerating pipe section 201b is communicated with the sixth interface 730, and an outlet end of the refrigerating pipe section 201b is communicated with the seventh interface 740. The two end openings of the second sub-section 220 are in communication with the eighth interface 750 and the ninth interface 760, respectively, e.g., the inlet end of the second sub-section 220 is in communication with the eighth interface 750 and the outlet end of the second sub-section 220 is in communication with the ninth interface 760.

It will be appreciated that the ninth port 760 may be in direct communication with the outlet end of the second sub-section 220 (i.e., the outlet end of the second pipe section 400), or the communication between the ninth port 760 and the outlet end of the second sub-section 220 may be via a conduit. Similarly, the eighth port 750 may be directly connected to the inlet end of the second sub-section 220 (i.e., the inlet end of the first pipe section 300), or the communication between the eighth port 750 and the inlet end of the second sub-section 220 may be implemented through a pipe.

When the fourth interface 710 is communicated with the ninth interface 760 and the fifth interface 720 is communicated with the eighth interface 750, the two ends of the heating pipe section 201a are communicated with the two ends of the second auxiliary section 220, that is, the inlet end of the heating pipe section 201a is communicated with the outlet end of the second auxiliary section 220 through the fourth interface 710 and the ninth interface 760, the outlet end of the heating pipe section 201a is communicated with the inlet end of the second auxiliary section 220 through the fifth interface 720 and the eighth interface 750, and correspondingly, the inlet end of the heating pipe section 201a is also communicated with the outlet end of the second pipe section 400 through the fourth interface 710 and the ninth interface 760, and the outlet end of the heating pipe section 201a is also communicated with the inlet end of the first pipe section 300 through the fifth interface 720 and the eighth interface 750.

When the sixth interface 730 is communicated with the ninth interface 760 and the seventh interface 740 is communicated with the eighth interface 750, both ends of the refrigerating pipe section 201b are communicated with both ends of the second sub-section 220, that is, the inlet end of the refrigerating pipe section 201b is communicated with the outlet end of the second sub-section 220 through the sixth interface 730 and the ninth interface 760, the outlet end of the refrigerating pipe section 201b is communicated with the inlet end of the second sub-section 220 through the seventh interface 740 and the eighth interface 750, and correspondingly, the inlet end of the refrigerating pipe section 201b is also communicated with the outlet end of the second pipe section 400 through the sixth interface 730 and the ninth interface 760, and the outlet end of the refrigerating pipe section 201b is also communicated with the inlet end of the first pipe section 300 through the seventh interface 740 and the eighth interface 750.

In this way, when the temperature of the structure to be tempered 20 or the device to be cooled 10 is insufficient, the corresponding interface in the second multi-way valve 700 may be connected to communicate the heating pipe section 201a in the temperature control pipe section 2011 with the two ends of the second sub-section 220, so that the cooling liquid in the second pipeline 200 or the first pipeline 100 may be heated by the heating pipe section 201a to raise the temperature of the cooling liquid flowing through the second heat exchanger 40 and the first heat exchanger 30, thereby raising the temperature of the structure to be tempered 20 or the device to be cooled 10 to the target temperature.

When the temperature of the structure to be tempered 20 or the device to be cooled 10 is too high, the corresponding interface in the second multi-way valve 700 is connected to communicate the refrigerating pipe section 201b in the temperature control pipe section 2011 with the two ends of the second sub-section 220, so that the cooling liquid in the second pipeline 200 or the first pipeline 100 can be cooled by the refrigerating pipe section 201b to reduce the temperature of the cooling liquid flowing through the second heat exchanger 40 and the first heat exchanger 30, thereby reducing the temperature of the structure to be tempered 20 or the device to be cooled 10 to the target temperature.

For example, when the structure to be tempered 20 (e.g. passenger cabin) and the device to be liquid cooled 10 are simultaneously heated, the fourth interface 710 may be controlled to communicate with the ninth interface 760, the fifth interface 720 may be controlled to communicate with the eighth interface 750, so as to communicate the heating pipe section 201a in the temperature control pipe section 2011 with both ends of the second sub-section 220, and the first operation mode of the thermal management system is switched to the heating mode, so that the second circulation loop 201 is switched to the heating loop 100a. In the first operation mode, the cooling fluid flowing out through the warm air core 40a may flow into the second sub-section 220 through the fifth port 720 and the eighth port 750 of the second multi-way valve 700, flow into the second main section 210b through the outlet end of the second sub-section 220 and the ninth port 760 and the fourth port 710 of the second multi-way valve 700, flow into the warm air core 40a after being heated by the condensing plate heat exchanger 211a and the electric heating core 221a, and be heated by the warm air core 40a and the air in the passenger compartment.

It will be appreciated that when the temperature of the cooling liquid in the first circulation loop 101 is insufficient, a portion of the cooling liquid in the heating loop 100a may be mixed into the cooling liquid in the first circulation loop 101 through the first pipe segment 300 to raise the temperature of the cooling liquid in the first circulation loop 101, so that the cooling liquid entering the first heat exchanger 30 (e.g., a battery pack cooling plate) can raise the temperature of the battery to within the first target temperature range.

When the structure 20 to be tempered (e.g. passenger cabin) and the device 10 to be cooled simultaneously cool, the sixth interface 730 may be controlled to communicate with the ninth interface 760, the seventh interface 740 may communicate with the eighth interface 750, so as to communicate the cooling pipe 201b in the temperature control pipe 2011 with both ends of the second sub-section 220, and switch to the cooling mode in the first operation mode of the thermal management system, so that the second circulation loop 201 is the cooling loop 100b, in the second operation mode, the cooling liquid flowing out through the second heat exchanger 40 (e.g. the cold air core 40 b) may flow into the second sub-section 220 through the seventh interface 740 and the eighth interface 750 of the second multi-way valve 700, and flow into the second main section 210b through the outlet end of the second sub-section 220 and the ninth interface 760 and the sixth interface 730 of the second multi-way valve 700, and then flow into the cold air core 40b after cooling through the evaporating plate heat exchanger 211b, and then flow into the cold air core 40b, so as to cool the air in the passenger cabin.

It will be appreciated that when the temperature of the cooling fluid in the first circulation loop 101 is too high, a portion of the cooling fluid in the refrigeration loop 100b may be mixed into the cooling fluid in the first circulation loop 101 through the first pipe segment 300 to reduce the temperature of the cooling fluid in the first circulation loop 101, so that the cooling fluid entering the first heat exchanger 30 (e.g., a battery pack cooling plate) can reduce the temperature of the battery to within the first target temperature range.

For another example, when the structure 20 to be tempered (e.g. the passenger cabin) is to be warmed separately, the fourth interface 710 may be controlled to communicate with the ninth interface 760, and the fifth interface 720 may be controlled to communicate with the eighth interface 750 to communicate the heating pipe section 201a of the temperature-controlled pipe section 2011 with both ends of the second sub-section 220, and the second operation mode of the thermal management system is switched to the heating mode, so that the second circulation loop 201 is switched to the heating loop 100a. In the second operation mode, the cooling fluid flowing out through the warm air core 40a may flow into the second sub-section 220 through the fifth port 720 and the eighth port 750 of the second multi-way valve 700, flow into the second main section 210b through the outlet end of the second sub-section 220 and the ninth port 760 and the fourth port 710 of the second multi-way valve 700, flow into the warm air core 40a after being heated by the condensing plate heat exchanger 211a and the electric heating core 221a, and be heated by the warm air core 40a and the air in the passenger compartment.

When the structure 20 to be tempered (e.g. passenger cabin) is cooled separately, the sixth interface 730 may be controlled to communicate with the ninth interface 760, the seventh interface 740 may be controlled to communicate with the eighth interface 750, so as to communicate the cooling pipe section 201b of the temperature control pipe section 2011 with both ends of the second sub-section 220, and switch the second operation mode of the thermal management system to a cooling mode, so that the second circulation loop 201 is the cooling loop 100b, in the second operation mode, the cooling liquid flowing out through the second heat exchanger 40 (e.g. the cold air core 40 b) may flow into the second sub-section 220 through the seventh interface 740 and the eighth interface 750 of the second multi-way valve 700, and flow into the second main section 210b through the outlet end of the second sub-section 220 and the ninth interface 760 and the sixth interface 730 of the second multi-way valve 700, and then flow into the cold air core 40b after cooling through the evaporating plate heat exchanger 211b, and then flow into the cold air core 40b, so as to cool the air in the passenger cabin.

For another example, when the liquid cooling device 10 is to be heated alone, the fourth interface 710 may be controlled to communicate with the ninth interface 760, and the fifth interface 720 may be controlled to communicate with the eighth interface 750, so as to communicate the heating pipe section 201a of the temperature-controlled pipe section 2011 with both ends of the second sub-section 220, and switch from the third operation mode of the thermal management system to the heating mode. In the third operation mode, the cooling liquid flowing out from the outlet end of the first heat exchanger 30 (e.g. the battery pack cooling plate) flows into the first heat exchanger 30 (e.g. the battery pack cooling plate) through the first main section 110b, the second pipe section 400, the ninth interface 760, the fourth interface 710, the second main section 210b, the warm air core 40a, the second main section 210a, the first pipe section 300 and the first main section 110a in sequence, so that the cooling liquid is heated by the second main section 210 (e.g. the condensing plate heat exchanger 211a and the electric heating core 221a on the second main section 210 b) and then enters the first heat exchanger 30 (e.g. the battery pack cooling plate), and then the device to be cooled 10 such as a battery can be heated, thereby ensuring that the device to be cooled 10 such as the battery is kept within the first target temperature range.

When the liquid cooling device 10 is to be cooled independently, the sixth interface 730 may be controlled to communicate with the ninth interface 760, and the seventh interface 740 may be controlled to communicate with the eighth interface 750, so as to communicate the cooling pipe 201b in the temperature-controlled pipe 2011 with two ends of the second sub-section 220, and switch from the third operation mode of the thermal management system to the cooling mode. In the third operation mode, the cooling liquid flowing out from the outlet end of the first heat exchanger 30 (e.g. the battery pack cooling plate) flows into the first heat exchanger 30 (e.g. the battery pack cooling plate) through the first main section 110b, the second pipe section 400, the ninth interface 760, the fourth interface 710, the second main section 210b, the cold air core 40b, the second main section 210a, the first pipe section 300 and the first main section 110a in sequence, so that the cooling liquid is cooled by the second main section 210 (e.g. the evaporating plate heat exchanger 211b on the second main section 210 b), and after the cooled cooling liquid enters the first heat exchanger 30 (e.g. the battery pack cooling plate), the device to be cooled 10 such as the battery can be cooled, thereby ensuring that the device to be cooled 10 such as the battery is kept within the first target temperature range.

With continued reference to fig. 19, in some examples, the condensing plate heat exchanger 211a in the heating tube segment 201a and the evaporating plate heat exchanger 211b in the cooling tube segment 201b may be arranged in series. Specifically, the inlet end of the condensation plate heat exchange core in the condensation plate heat exchanger 211a is communicated with the outlet end of the evaporation plate heat exchange core in the evaporation plate heat exchanger 211b, and the inlet end of the evaporation plate heat exchange core is communicated with the outlet end of the condensation plate heat exchange core, so that the recycling of the refrigerant (such as the refrigerant) can be realized, and the cost of the thermal management system is saved. In addition, it is possible to ensure that the refrigerant in the condensation plate heat exchanger 211a is in a high temperature gas state during each heating process or that the refrigerant in the evaporation plate heat exchanger 211b is in a low temperature liquid state during each cooling process.

For example, when the thermal management system is in the heating mode, the gaseous refrigerant in the condensation plate heat exchange core condenses to release heat to the cooling liquid each time the cooling liquid passes through the condensation plate heat exchanger 211a, so that the temperature of the refrigerant is reduced, and a liquid refrigerant is formed, and the liquid refrigerant can flow into the evaporation plate heat exchange core of the evaporation plate heat exchanger 211b, evaporate through the evaporation plate heat exchange core to form a gaseous state, and then flow into the condensation plate heat exchange core to perform condensation heat release, thus repeatedly circulating.

Accordingly, when the thermal management system is in the cooling mode, the liquid refrigerant in the evaporating plate heat exchange core absorbs heat of the cooling liquid to evaporate each time the cooling liquid passes through the evaporating plate heat exchanger 211b, so that the temperature of the refrigerant is increased, and a gaseous refrigerant is formed, and the gaseous refrigerant can flow into the condensing plate heat exchange core of the condensing plate heat exchanger 211a, be condensed into a liquid state by the condensing plate heat exchange core, then flow into the evaporating plate heat exchange core of the evaporating plate heat exchanger 211b to evaporate and absorb heat, and thus the cycle is repeated.

When the evaporator plate heat exchange device is arranged, the condensing plate heat exchange core and the evaporating plate heat exchange core can be communicated through the third pipeline 800, for example, the inlet end of the condensing plate heat exchange core is communicated with the outlet end of the evaporating plate heat exchange core through one of the third pipelines 800, and the inlet end of the evaporating plate heat exchange core is communicated with the outlet end of the condensing plate heat exchange core through the other third pipeline 800, so that the refrigerant circularly flows in a fourth circulation loop formed by the third pipeline 800, the condensing plate heat exchange core and the evaporating plate heat exchange core.

In some examples, a third water pump 810 may be disposed on the third pipeline 800, where the third water pump 810 is configured to provide kinetic energy to the refrigerant (e.g., refrigerant) to ensure smooth flow of the refrigerant between the condensation plate heat exchanger 211a and the evaporation plate heat exchanger 211b in the fourth circulation loop. In addition, the mass flow rate of the refrigerant into the condensing plate heat exchanger 211a or the evaporating plate heat exchanger 211b may be controlled by adjusting the rotation speed of the third water pump 810.

Referring to fig. 19, the thermal management system of the embodiment of the present application may further include a fourth pipe 900, and both ends of the fourth pipe 900 may communicate with both ends of the first heat exchanger 30 (e.g., a battery pack cold plate), i.e., the fourth pipe 900 and the first pipe 100 are disposed in parallel. For example, the openings at both ends of the fourth pipeline 900 are respectively communicated with the second openings of the two first main sections 110, and the fourth pipeline 900, the two first main sections 110 and the first heat exchanger 30 together form a heat dissipation circuit. For example, the inlet end of the fourth conduit 900 communicates with the second end of the first main section 110b and the outlet end of the fourth conduit 900 communicates with the second end of the first main section 110 a.

The fourth pipeline 900 is provided with a radiator 910, an inlet end of the radiator 910 is communicated with an inlet end of the fourth pipeline 900, and an outlet end of the radiator 910 is communicated with an outlet end of the fourth pipeline 900. When the temperature of the device 10 to be cooled (e.g., a battery) is too high, the heat of the battery can be transferred to the cooling liquid through the first heat exchanger 30, and the cooling liquid can be transferred into the radiator 910 under the driving of the second water pump 111, and the radiator 910 dissipates the heat of the cooling liquid into the environment to reduce the temperature of the battery.

In this embodiment, the heat spreader 910 may be a tube-type heat spreader or an electronic heat spreader in the related art, and the structure of the heat spreader 910 is not limited here.

When provided, the second multi-way valve 700 may include a tenth interface 770 and an eleventh interface 780. Wherein, the openings at both ends of the fourth pipeline 900 are respectively communicated with the tenth interface 770 and the eleventh interface 780, for example, the inlet end of the fourth pipeline 900 is communicated with the tenth interface 770 and the outlet end of the fourth pipeline 900 is communicated with the eleventh interface 780.

Thus, when the heat sink 910 of the fourth pipeline 900 is required to radiate heat from the battery in the battery pack, the tenth interface 770 may be communicated with the ninth interface 760, and the eleventh interface 780 may be communicated with the eighth interface 750, so that the inlet end of the fourth pipeline 900 is communicated with the outlet end of the first main section 110 through the second pipe section 400, and the outlet end of the fourth pipeline 900 is communicated with the inlet end of the first main section 110 through the first pipe section 300, so that the fourth pipeline 900, the two first main sections 110 and the first heat exchanger 30 (e.g. the battery pack cold plate) may form a heat radiation loop, so that the heat sink 910 radiates heat from the battery.

In addition, the openings at both ends of the fourth pipeline 900 are communicated with the tenth interface 770 and the eleventh interface 780 of the second multi-way valve 700, so that the heat dissipation mode of the battery pack can be adjusted at any time according to actual needs, and the mode switching of the thermal management system is convenient and the process is simple.

With continued reference to fig. 19, the thermal management system according to the embodiment of the present application may further include a fifth pipeline 1000, where the fifth pipeline 1000 has a power assembly 1100 and a fourth water pump 1200 thereon, where the power assembly 1100 includes a power assembly device and a heat dissipation channel, the heat dissipation channel is located in the power assembly device, an inlet end of the heat dissipation channel is communicated with an inlet end of the fifth pipeline 1000, an outlet end of the heat dissipation channel is communicated with an outlet end of the fifth pipeline 1000, and the fourth water pump 1200 is connected in series with the fifth pipeline 1000. And the heat dissipation pipes are communicated with the pipes of the fifth pipeline 1000, and are all used for circulating cooling liquid,

the heat dissipation channel and the pipeline of the fifth pipeline 1000 are used for circulating cooling liquid. The powertrain 1100 may include a motor, an inverter, a distribution box, and the like.

For example, the second multi-way valve 700 may include a twelfth port 790, an inlet end of the fifth pipe 1000 being in communication with an outlet end of the radiator 910, and an outlet end of the fifth pipe 1000 being in communication with the twelfth port 790.

In some possible embodiments, when the twelfth interface 790 is communicated with the tenth interface 770, the outlet end of the fifth pipeline 1000 is convenient to communicate with the inlet end of the fourth pipeline 900, so that the fourth pipeline 900 and the fifth pipeline 1000 form a heat dissipation loop of the power assembly, and thus, after the heat of the device of the power assembly 1100 is transferred into the cooling liquid in the heat dissipation channel, the heat can be transferred into the radiator 910 through the fourth water pump 1200, and the radiator 910 dissipates the heat into the environment, thereby realizing the heat dissipation effect on the device in the power assembly 1100.

In other possible embodiments, the fifth line 1000 may be in communication with a temperature-controlled pipe segment 2011, through which temperature-controlled components on the temperature-controlled pipe segment 2011 regulate the temperature of the powertrain 1100 in the fifth line 1000.

For example, when the fourth port 710 of the second multi-way valve 700 is communicated with the twelfth port 790 and the fifth port 720 is communicated with the eleventh port 780, the heating pipe section 201a may be communicated with the fifth pipeline 1000, so that the inlet end of the heating pipe section 201a is communicated with the outlet end of the fifth pipeline 1000, and the outlet end of the heating pipe section 201a is communicated with the inlet end of the fifth pipeline 1000, so that the heating pipe section 201a and the fifth pipeline 1000 may form a fifth circulation loop, and the cooling liquid in the fifth circulation loop may be heated by the condensing plate heat exchanger 211a in the heating pipe section 201a, thereby ensuring that the cooling liquid entering the power assembly can heat the structural components of the power assembly, ensuring that the power assembly is in a proper temperature range, and further improving the working efficiency of the power assembly.

For another example, when the sixth port 730 of the second multi-way valve 700 is communicated with the twelfth port 790 and the seventh port 740 is communicated with the eleventh port 780, the refrigeration pipe section 201b may be communicated with the fifth pipeline 1000, so that the inlet end of the refrigeration pipe section 201b is communicated with the outlet end of the fifth pipeline 1000, and the outlet end of the refrigeration pipe section 201b is communicated with the inlet end of the fifth pipeline 1000, so that the refrigeration pipe section 201b and the fifth pipeline 1000 may form a fifth circulation loop, and the cooling liquid in the fifth circulation loop may be cooled by the evaporating plate heat exchanger 211b in the refrigeration pipe section 201b, thereby ensuring that the cooling liquid entering the power assembly can cool and dissipate heat of the structural members of the power assembly, ensuring that the power assembly is in a proper temperature range, and further improving the working efficiency of the power assembly.

According to the battery provided by the embodiment of the application, the first heat exchanger 30 (such as the battery pack cold plate) in the thermal management system is in thermal contact with the battery so as to realize temperature control of the battery and ensure that the battery is at a proper temperature.

It should be noted that, the numerical values and the numerical ranges referred to in the embodiments of the present application are approximate values, and may have a certain range of errors under the influence of the manufacturing process, and those errors may be considered to be negligible by those skilled in the art.

The foregoing is merely illustrative embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think about changes or substitutions within the technical scope of the present application, and should be covered in the scope of the present application; embodiments of the present application and features of embodiments may be combined with each other without conflict. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

It should be understood that in the present application, "connected", "in communication" may refer to a mechanical connection or a physical connection, i.e., a and B connection or a and B connection may refer to a fastening member (such as a screw, bolt, rivet, etc.) between a and B, or a and B contact each other and a and B are difficult to separate. In addition, "communication" means that a communicates with B in some states, but not in any state where a and B are always in communication.

In the description of the embodiments of the present application, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and for example, "connected" may be either detachably connected or non-detachably connected; can be in direct contact connection or indirect connection through an intermediate medium, and can be communication between two elements or interaction relationship between two elements. The specific meaning of the above terms in the embodiments of the present application will be understood by those of ordinary skill in the art according to the specific circumstances. References to directional terms in the embodiments of the present application, such as "upper", "lower", "left", "right", "inner", "outer", etc., are merely with reference to the directions of the drawings, and thus, the directional terms are used in order to better and more clearly describe and understand the embodiments of the present application, rather than to indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the embodiments of the present application. "plurality" means at least two.

In the embodiment of the present application, "and/or" is merely an association relationship describing an association object, and indicates that three relationships may exist, for example, a and/or B may indicate: a exists alone, A and B exist together, and B exists alone. In addition, the character "/" herein generally indicates that the front and rear associated objects are an "or" relationship.

The terms first, second, third, fourth and the like in the description and in the claims of embodiments of the application and in the above-described figures, if any, are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order.

Reference in the specification to "one embodiment" or "some embodiments" or the like means that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," and the like in the specification are not necessarily all referring to the same embodiment, but mean "one or more but not all embodiments" unless expressly specified otherwise. The terms "comprising," "including," "having," and variations thereof mean "including but not limited to," unless expressly specified otherwise.

Claims

1. A thermal management system, comprising:

the first heat exchanger is used for exchanging heat with the device to be cooled, and the inlet end of the first heat exchanger is communicated with the outlet end of the first heat exchanger through a first pipeline;

the second heat exchanger is used for exchanging heat with the structure to be temperature-regulated, and the inlet end of the second heat exchanger is communicated with the outlet end of the second heat exchanger through a second pipeline;

the inlet end of the first pipe section is communicated with the second pipeline and is connected in series with the outlet end of the second heat exchanger; the outlet end of the first pipe section is communicated with the first pipeline and is connected in series with the inlet end of the first heat exchanger; the inlet end of the second pipe section is communicated with the first pipeline and is connected in series with the outlet end of the first heat exchanger; the outlet end of the second pipe section is communicated with the second pipeline and is connected in series with the inlet end of the second heat exchanger;

a first multi-way valve comprising a first port, a second port, and a third port;

the inlet end of the first pipe section is communicated with the second pipeline through the first interface, and the first multi-way valve is connected in series on the second pipeline through the second interface and the third interface; or the inlet end of the second pipe section is communicated with the first pipeline through the first interface, and the first multi-way valve is connected in series on the first pipeline through the second interface and the third interface;

The first interface, the second interface and the third interface of the first multi-way valve are used for being conducted in a first working mode, so that the first pipeline and the first heat exchanger form a first circulation loop, the second pipeline and the second heat exchanger form a second circulation loop, cooling liquid in the second circulation loop is mixed with cooling liquid in the first circulation loop through the first pipe section, cooling liquid in the first circulation loop is mixed with cooling liquid in the second circulation loop through the second pipe section, and the first working mode is a mode that both the first heat exchanger and the second heat exchanger are in a working state.

2. The thermal management system of claim 1, wherein the second piping comprises a second secondary section and two second primary sections, wherein a first end of one of the second primary sections is in communication with an outlet end of the second heat exchanger, a second end of one of the second primary sections is in communication with an inlet end of the second secondary section and an inlet end of the first pipe section, respectively, a first end of the other of the second primary sections is in communication with an inlet end of the second heat exchanger, and a second end of the other of the second primary sections is in communication with an outlet end of the second secondary section and an outlet end of the second pipe section, respectively;

The temperature control assembly and the first water pump are connected in series on the second pipeline, the temperature control assembly is connected in series on the second main section of the inlet end of the second heat exchanger, one end of the temperature control assembly is communicated with the inlet end of the second heat exchanger, and the other end of the temperature control assembly is communicated with the outlet end of the first water pump.

3. The thermal management system of claim 2, wherein the first water pump is connected in series between an outlet end of the second pipe segment and the temperature control assembly.

4. A thermal management system according to any one of claims 1-3, wherein said first conduit comprises a first secondary section and two first primary sections, wherein a first end of one of said first primary sections communicates with an inlet end of said first heat exchanger, a second end of one of said first primary sections communicates with an outlet end of said first secondary section and an outlet end of said first tube section, respectively, a first end of the other of said first primary sections communicates with an outlet end of said first heat exchanger, and a second end of the other of said first primary sections communicates with an inlet end of said first secondary section and an inlet end of said second tube section, respectively;

the first pipeline is provided with a second water pump, and the second water pump is connected in series with the first main section.

5. The thermal management system of claim 4, wherein an inlet end of the second water pump communicates with an outlet end of the first pipe section, and an outlet end of the second water pump communicates with an inlet end of the first heat exchanger.

6. The thermal management system of any of claims 2-5, further comprising: a switch valve;

the first multi-way valve is connected in series on the second pipeline, the switch valve is connected in series on a first auxiliary section of the first pipeline, the inlet end of the switch valve is communicated with the inlet end of the first auxiliary section, the outlet end of the switch valve is communicated with the outlet end of the first auxiliary section, the switch valve is used for being conducted in a first working mode so that the first pipeline and the first heat exchanger form a first circulation loop, and the switch valve is used for being turned off in a third working mode so that the first heat exchanger, the two first main sections, the second pipe sections, the second heat exchanger, the two second main sections and the first pipe section form a third circulation loop;

or the first multi-way valve is connected in series on the first pipeline, the switch valve is connected in series on the second auxiliary section of the second pipeline, the inlet end of the switch valve is communicated with the inlet end of the second auxiliary section, the outlet end of the switch valve is communicated with the outlet end of the second auxiliary section, the switch valve is used for conducting in a first working mode and a second working mode so as to enable the first pipeline and the first heat exchanger to form a first circulation loop, the second pipeline and the second heat exchanger to form a second circulation loop, and the switch valve is used for being turned off in a third working mode so as to enable the first heat exchanger, the two first main sections, the second pipe sections, the second heat exchanger, the two second main sections and the first pipe sections to form a third circulation loop;

The second working mode is a mode that the second heat exchanger is in a working state and the second heat exchanger is in a non-working state, and the third working mode is a mode that the first heat exchanger is in a working state and the second heat exchanger is in a non-working state.

7. The thermal management system of claim 6, wherein the on-off valve is a one-way valve or a shut-off valve.

8. The thermal management system of any of claims 1-7, wherein the first multi-way valve is a proportional three-way valve.

9. The thermal management system of any of claims 1-8, further comprising a second multi-way valve comprising a fourth interface, a fifth interface, a sixth interface, a seventh interface, an eighth interface, and a ninth interface;

the two second main sections of the second pipeline and the second heat exchanger form temperature control pipe sections, the number of the temperature control pipe sections is two, the two temperature control pipe sections comprise refrigerating pipe sections and heating pipe sections, two ends of the heating pipe sections are respectively communicated with the fourth interface and the fifth interface, and two ends of the refrigerating pipe sections are respectively communicated with the sixth interface and the seventh interface; two ends of a second auxiliary section of the second pipeline are respectively communicated with the eighth interface and the ninth interface;

The two ends of the heating pipe section are communicated with the ninth interface at the fourth interface, and the five interfaces are communicated with the two ends of the second auxiliary section when being communicated with the eighth interface; the two ends of the refrigeration pipe section are communicated with the ninth interface at the sixth interface, and the seventh interface is communicated with the two ends of the second auxiliary section when the seventh interface is communicated with the eighth interface.

10. The thermal management system of claim 9, wherein the second heat exchanger of the heating tube segment is a warm air core and the temperature control assembly of the heating tube segment comprises at least one of a condensing plate heat exchanger and an electrical heating core.

11. The thermal management system of claim 9 or 10, wherein the second heat exchanger of the refrigeration tube segment is a cold air core and the temperature control assembly of the refrigeration tube segment comprises an evaporating plate heat exchanger.

12. The thermal management system of any one of claims 9-11, wherein the cold plate heat exchanger in the heating tube section has a cold plate heat exchanger core, the cold plate heat exchanger in the cooling tube section has an evaporator plate heat exchanger core, an inlet end of the cold plate heat exchanger core is in communication with an outlet end of the evaporator plate heat exchanger core, and an inlet end of the evaporator plate heat exchanger core is in communication with an outlet end of the cold plate heat exchanger core;

The condensing plate heat exchange core and the evaporating plate heat exchange core are both used for circulating refrigerant.

13. The thermal management system of any of claims 1-12, wherein the first heat exchanger is a battery pack cold plate in thermal contact with a battery of the battery pack.

14. A vehicle comprising a battery and the thermal management system of any one of claims 1-13;

a first heat exchanger of a first conduit in the thermal management system is in thermal contact with the battery.

15. The vehicle of claim 14, further comprising a passenger compartment;

a second heat exchanger of a second pipeline in the thermal management system is positioned in the passenger cabin.