CN114074584A

CN114074584A - Thermal management system

Info

Publication number: CN114074584A
Application number: CN202011331076.4A
Authority: CN
Inventors: 不公告发明人
Original assignee: Sanhua Holding Group Co Ltd
Current assignee: Sanhua Holding Group Co Ltd
Priority date: 2020-08-21
Filing date: 2020-11-24
Publication date: 2022-02-22

Abstract

The invention discloses a heat management system, which comprises a compressor, a first heat exchanger, a first heat management unit, a second heat management unit and a first dual-flow-channel heat exchanger, wherein the first dual-flow-channel heat exchanger comprises a first flow channel and a second flow channel, refrigerant in the first flow channel and refrigerant in the second flow channel can exchange heat, the second heat management unit comprises at least one throttling valve and a second heat exchanger, the at least one throttling valve comprises a first regulating valve and can regulate the pressure of the refrigerant in the second heat exchanger, the first regulating valve is arranged between the first heat exchanger and the second heat exchanger along the flowing direction of working medium, the first flow channel is arranged between the first heat exchanger and the second heat exchanger, and the second flow channel is arranged between the second heat exchanger and the compressor; this relatively improves the temperature uniformity of the second heat exchanger.

Description

Thermal management system

Technical Field

The invention relates to the technical field of thermal management, in particular to a thermal management system.

Background

The thermal management system for the vehicle comprises the heat exchanger capable of adjusting the temperature of the battery, and the temperature uniformity of the heat exchanger has great influence on the performance of the battery, so that new requirements are provided for the thermal management system to ensure that the battery works in a relatively uniform temperature environment.

Disclosure of Invention

The invention aims to provide a heat management system which is beneficial to improving the temperature uniformity of a heat exchanger.

The embodiment of the invention provides a heat management system, which comprises a compressor and a first heat exchanger, wherein a first port of the compressor is connected with a second port of the first heat exchanger, the heat management system further comprises a first heat management unit, a second heat management unit and a first dual-channel heat exchanger, at least parts of the first heat management unit and the second heat management unit and the first dual-channel heat exchanger are all positioned between the second port of the compressor and the first port of the first heat exchanger along the flowing direction of a working medium in the heat management system, the first heat management unit can exchange heat with a first heat generating source, the second heat management unit can exchange heat with a second heat generating source, the first dual-channel heat exchanger comprises a first channel and a second channel, and the refrigerant in the first channel can exchange heat with the refrigerant in the second channel, the second thermal management unit comprising at least one throttling valve and a second heat exchanger, the at least one throttling valve comprising a first regulating valve capable of regulating the pressure of refrigerant in the second heat exchanger,

the first regulating valve is arranged between the first heat exchanger and the second heat exchanger, the first flow channel is arranged between the first heat exchanger and the second heat exchanger, and the second flow channel is arranged between the second heat exchanger and the compressor along the flowing direction of working media in the heat management system.

According to the heat management system provided by the embodiment of the invention, the heat management system comprises the first heat management unit, the refrigerant unit of the second heat management unit and the first dual-channel heat exchanger, and by arranging the first heat management unit and the second heat management unit, the heat management system can exchange heat with different heat sources, for example, different heat sources are refrigerated, so that the universality of the heat management system is improved; the refrigerant unit of the second heat management unit comprises a first regulating valve and a second heat exchanger, the first regulating valve can regulate the flow and the pressure of the refrigerant entering the second heat exchanger, and the second heat exchanger can be matched with the heat load of the heat generating source; in the extending direction of the refrigerant transferring passage, by arranging the first flow passage of the first dual-flow passage heat exchanger between the first heat exchanger and the second heat exchanger, arranging the second flow passage between the second heat exchanger and the compressor, when the second heat exchanger is used for refrigerating, the high-temperature and high-pressure refrigerant flowing out of the first heat exchanger enters the second heat exchanger through the first flow passage, the low-temperature and low-pressure refrigerant flowing out of the second heat exchanger enters the compressor through the second flow passage, and the relatively cold refrigerant and the relatively hot refrigerant exchange heat in the first double-flow-passage heat exchanger, so that the superheat degree of the refrigerant flowing out of the second heat exchanger can be reduced, so that the temperature difference between the outlet and the inlet of the second heat exchanger is reduced, the temperature uniformity of the second heat exchanger is relatively improved, meanwhile, the superheat degree of the refrigerant entering the compressor can be ensured, and the service life of the compressor is prolonged.

Drawings

FIG. 1 is a schematic connection block diagram of a thermal management system provided in a first embodiment of the present invention;

FIG. 2 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 1;

FIG. 3 is a schematic connection block diagram of a thermal management system provided in a second embodiment of the present invention;

FIG. 4 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 3;

FIG. 5 is a schematic connection block diagram of a thermal management system provided in a third embodiment of the present invention;

FIG. 6 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 5;

FIG. 7 is a schematic connection block diagram of a thermal management system provided in a fourth embodiment of the present invention;

FIG. 8 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 7;

FIG. 9 is a schematic connection block diagram of a thermal management system provided by a fifth embodiment of the present invention;

FIG. 10 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 9;

FIG. 11 is a schematic connection block diagram of a thermal management system provided by a sixth embodiment of the present invention;

FIG. 12 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 11;

FIG. 13 is a schematic connection block diagram of a thermal management system provided in a seventh embodiment of the present invention;

FIG. 14 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 13;

FIG. 15 is a schematic connection block diagram of a thermal management system provided by an eighth embodiment of the present invention;

FIG. 16 is a schematic pressure enthalpy diagram corresponding to the thermal management system provided in FIG. 15;

FIG. 17 is a schematic connection block diagram of a thermal management system provided in a ninth embodiment of the present invention;

FIG. 18 is a schematic illustration of a first valve arrangement provided in accordance with an embodiment of the present invention;

FIG. 19 is a schematic refrigerant flow diagram of the thermal management system shown in FIG. 17 with the second heat exchanger heating;

FIG. 20 is a refrigerant flow schematic of the thermal management system shown in FIG. 17 with the second heat exchanger cooling;

FIG. 21 is a schematic connection block diagram of a thermal management system provided in a tenth embodiment of the present invention;

FIG. 22 is a schematic connection block diagram of a thermal management system provided in an eleventh embodiment of the present invention;

FIG. 23 is a schematic flow diagram of the refrigerant and coolant of the heat management system of FIG. 22 in a heat recovery mode;

FIG. 24 is a schematic flow diagram of the refrigerant and coolant for the heat management system of FIG. 22 with the second heat exchanger cooling and the compressor on;

FIG. 25 is a schematic view of the construction of the second heat exchanger shown in FIG. 22;

FIG. 26 is a schematic flow diagram of the cooling fluid of the heat management system of FIG. 22 with the second heat exchanger cooling and the compressor off.

Detailed Description

Features and exemplary embodiments of various aspects of the present invention will be described in detail below, and in order to make objects, technical solutions and advantages of the present invention more apparent, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

The thermal management system in the technical scheme of the invention can be implemented in various ways, at least one of which can be applied to a vehicle thermal management system, at least one of which can be applied to other thermal management systems such as a household thermal management system or a commercial thermal management system, and the thermal management principle of the thermal management system applied to the vehicle thermal management system, the household thermal management system or the commercial thermal management system is similar, and the vehicle thermal management system is taken as an example and is explained with reference to the attached drawings. Specifically, the thermal management system of the embodiment of the invention may be applied to cooling of electrical equipment in a hybrid vehicle powered by an engine and a motor, and may also be applied to cooling of electrical equipment in a vehicle powered by only a motor, where the hybrid vehicle and the electric-only vehicle are both referred to as electric vehicles.

Referring to fig. 1, fig. 3 and fig. 5 together, fig. 1 is a schematic connection block diagram of a thermal management system according to a first embodiment of the present invention, fig. 3 is a schematic connection block diagram of a thermal management system according to a second embodiment of the present invention, and fig. 5 is a schematic connection block diagram of a thermal management system according to a third embodiment of the present invention. The embodiment of the invention provides a thermal management system 1 which comprises an in-vehicle temperature and a battery temperature, wherein the in-vehicle temperature can be used for thermally managing the in-vehicle temperature of a vehicle, the battery temperature can be used for thermally managing the battery temperature of an electric vehicle, and the thermal management system 1 can be arranged on the electric vehicle. Specifically, the working medium of the in-vehicle temperature and the battery temperature may be a refrigerant, which enables in-vehicle cooling and/or heating, and cooling and/or heating of the battery.

The thermal management system 1 provided in the embodiment of the present invention may include a refrigerant system and a coolant system, or may include only a refrigerant system, where a working medium in the refrigerant system is a refrigerant and a working medium in the coolant system is a coolant.

The thermal management system 1 comprises a compressor 100 and a first heat exchanger 700, wherein a first port 101 of the compressor 100 is connected with a second port 702 of the first heat exchanger 700. When the thermal management system 1 starts a cooling mode, the working medium can be transmitted from the first port 101 of the compressor 100 to the second port 702 of the first heat exchanger 700, and exchanges heat with the outside atmosphere through the first heat exchanger 700, and when circulating in the thermal management system 1, the working medium passing through the first port 701 of the first heat exchanger 700 can exchange heat with different heat sources, such as cooling and/or heating the inside of the vehicle and cooling and/or heating a battery on the electric vehicle, and the working medium after heat exchange returns to the second port 102 of the compressor 100, so that the thermal management system 1 can operate in a circulating manner.

The thermal management system 1 further comprises a first thermal management unit 300, a second thermal management unit 5000 and a first dual-channel heat exchanger 600, the first thermal management unit 300 is capable of exchanging heat with a first heat generating source, the second thermal management unit 5000 is capable of exchanging heat with a second heat generating source, at least part of the first thermal management unit 300 and the second thermal management unit 5000 and the first dual-channel heat exchanger 600 are located between a first port 701 of the first heat exchanger 700 and a second port 102 of the compressor, after the working medium flows out of the first port 701 of the first heat exchanger 700, the working medium passes through the first thermal management unit 300, the first part of the second thermal management unit 5000 and the first dual-channel heat exchanger 600, and then back to the second port 102 of the compressor 100, the thermal management system 1 is in a cooling mode, the first thermal management unit 300, a first portion of the second thermal management unit 5000, and the first dual channel heat exchanger 600 are located downstream of the first heat exchanger 700. It is understood that "upstream" and "downstream" are defined herein with respect to the direction of flow of the working medium, e.g., the first thermal management unit 300 being downstream of the first heat exchanger 700 means that in the cooling mode, the working medium flows first through the first heat exchanger 700 and then through the first thermal management unit 300; the first heat exchanger 700 is located upstream of the first thermal management unit 300, meaning that in the cooling mode, the working medium flows through the first heat exchanger 700 before passing through the first thermal management unit 300.

The first thermal management unit 300 and the second thermal management unit 5000 are respectively capable of exchanging heat with different heat sources, the first dual-channel heat exchanger 600 comprises a first channel 601 and a second channel 602, the working medium in the first channel 601 can exchange heat with the working medium in the second channel 602, the second thermal management unit 5000 comprises at least one throttle and a second heat exchanger 500, the at least one throttle comprises a first regulating valve 440, the first regulating valve 440 is used for regulating the pressure and the flow of the refrigerant in the refrigerant channel of the second heat exchanger 500, in the flow direction of the working medium in the thermal management system 1, the first regulating valve 440 is located between the first heat exchanger 700 and the second heat exchanger 500, the first flow channel 601 is located between the first heat exchanger 700 and the second heat exchanger 500, and the second flow channel 602 is located between the second heat exchanger 500 and the second port 102 of the compressor 100. The first thermal management unit 300 may be used for cooling or heating in the vehicle, and the second thermal management unit 5000 may be used for cooling or heating a battery on the electric vehicle.

According to the thermal management system 1 provided by the embodiment of the present invention, the first regulating valve 440 can regulate the flow of the working medium entering the second heat exchanger 500, so that the second heat exchanger 500 can be matched with the heat load of the heat source (battery); in the flowing direction of the working medium, the first flow channel 601 of the first dual-flow-channel heat exchanger 600 is located between the first heat exchanger 700 and the second heat exchanger 500, and the second flow channel 602 is located between the second heat exchanger 500 and the second port 102 of the compressor 100, so that when the second heat exchanger 500 is refrigerating, the working medium with high temperature and high pressure flowing out of the first heat exchanger 700 enters the second heat exchanger 500 through the first flow channel 601, the refrigerant with low temperature and low pressure flowing out of the second heat exchanger 500 passes through the second flow channel 602, and the relatively cold refrigerant and the relatively hot refrigerant exchange heat in the first dual-flow-channel heat exchanger 600, the superheat degree of the refrigerant flowing out of the second heat exchanger 500 can be reduced, the temperature difference between the outlet and the inlet of the second heat exchanger 500 is reduced, the temperature uniformity of the second heat exchanger 500 is relatively improved, and the superheat degree of the refrigerant entering the compressor 100 can meet the requirement at the same time, the service life of the compressor 100 is improved.

In some embodiments, the compressor 100 can be located on a motor or an engine of an electric vehicle such that the motor or the engine can provide a power source for the compressor 100 to operate the compressor 100. The compressor is capable of circulating a refrigerant in the thermal management system 1.

The first heat exchanger 700 can condense (liquefy) the superheated refrigerant gas compressed in the compressor 100 by radiating heat to the outside air and cooling the gas. Alternatively, the first heat exchanger 700 may be a condenser, and the first heat exchanger 700 includes channels through which a refrigerant circulates, and fins capable of increasing a heat exchange area between the refrigerant flowing in the channels and air around the first heat exchanger 700.

In an implementation, the first heat exchanger 700 is used for exchanging heat between cooling air and refrigerant flowing in the first heat exchanger 700. Here, the cooling air may be supplied to the first heat exchanger 700 by natural cooling air generated during the traveling of the electric vehicle. Alternatively, the thermal management system 1 may further include a fan that supplies cooling air to the first heat exchanger 700 so that the first heat exchanger 700 exchanges heat with the atmosphere, and the refrigerant is liquefied after flowing through the first heat exchanger 700.

Optionally, the first thermal management unit 300 may be configured to perform thermal management on the temperature inside the vehicle, and the first thermal management unit 300 may include a third regulating valve 420 and a third heat exchanger 310, where the third regulating valve 420 is configured to regulate the flow rate and pressure of the refrigerant entering the third heat exchanger 310, and the third heat exchanger 310 performs heat exchange between the refrigerant and the air inside the vehicle to implement cooling of the vehicle by the refrigerant.

The second thermal management unit 5000 may be used for thermal management of a battery in an electric vehicle, and the first regulating valve 440 may be an expansion valve that changes the high-pressure liquid-phase refrigerant flowing through the pipe into a low-temperature low-pressure mist-like refrigerant by expanding the refrigerant, which is in a gas-liquid two-phase region. The first regulating valve 440 decompresses the refrigerant liquid condensed by the first heat exchanger 700 into wet vapor in a gas-liquid mixed state, the wet vapor in the gas-liquid mixed state enters the second heat exchanger 500, and a refrigerant flow passage of the second heat exchanger 500 may be a direct cooling plate that is in direct contact or indirect contact with a battery to refrigerate the battery.

In order to achieve independent thermal management of the first thermal management unit 300 and the second thermal management unit 5000, please further refer to fig. 1, fig. 3 and fig. 5, in some embodiments, the thermal management system 1 includes a first main circuit 10, a first branch circuit 20, a second branch circuit 30 and a second main circuit 40, a first port 701 of the first heat exchanger 700 is respectively communicated with the first branch circuit 20 and the second branch circuit 30 through the first main circuit 10, the first branch circuit 20 and the second branch circuit 30 are respectively communicated with the second port 102 of the compressor 100 through the second main circuit 40, the first branch circuit 20 and the second branch circuit 30 can be arranged in parallel, the first thermal management unit 300 is arranged in the first branch circuit 20, and the first regulating valve 440 and the second heat exchanger 500 of the second thermal management unit 5000 are arranged in the second branch circuit 30. With the above arrangement, the refrigerant of the thermal management system 1 can be respectively transmitted to the first branch circuit 20 and the second branch circuit 30 through the first main circuit 10, so that the first thermal management unit 300 disposed on the first branch circuit 20 and the second thermal management unit 5000 disposed on the second branch circuit 30 respectively and independently adjust the circulation condition of the working medium, thereby realizing independent thermal management of the respective branch circuits.

Based on this, as shown in fig. 1 and fig. 3, the first dual channel heat exchanger 600 may be disposed on the second branch 30, or as shown in fig. 5, the first channel 601 of the first dual channel heat exchanger 600 is disposed on the first trunk 10, and the second channel 602 of the first dual channel heat exchanger 600 is disposed on the second trunk 40. Through the arrangement, the refrigerant in the first flow channel 601 and the refrigerant in the second flow channel 602 in the first dual-flow-channel heat exchanger 600 can exchange heat, the embodiment of fig. 1 and 3 is beneficial to reducing the superheat degree of the refrigerant flowing out of the second heat exchanger 500, the condition that the refrigerant at the position is almost in a gas phase state and cannot be well refrigerated with a battery heat source at the outlet position when the superheat degree of the outlet of the second heat exchanger 500 is large is improved, the temperature difference between the outlet and the inlet of the second heat exchanger 500 is reduced, the temperature uniformity of the second heat exchanger 500 is relatively improved, the temperature uniformity of a battery is also improved, meanwhile, after the refrigerant circulates through the second flow channel 602, the superheat degree of the refrigerant entering the compressor 100 can be improved, and the service life of the compressor 100 is prolonged. The embodiment of fig. 5 is advantageous to reduce the superheat degree of the refrigerant flowing out of the second heat exchanger 500 and the superheat degree of the refrigerant flowing out of the third heat exchanger 310, so that the temperature uniformity of the second heat exchanger 500 and the temperature uniformity in the vehicle are relatively improved, and the superheat degree of the refrigerant entering the compressor 100 is also improved, so that the service life of the compressor 100 is prolonged.

When the first dual flow channel heat exchanger 600 is disposed on the second branch circuit 30, optionally, on the second branch circuit 30, i.e., in the extending direction of the second branch circuit 30, the first flow channel 601 is disposed between the first main circuit 10 and the first regulating valve 440 or between the first regulating valve 440 and the refrigerant flow channel of the second heat exchanger 500, and the second flow channel 602 is disposed between the refrigerant flow channel of the second heat exchanger 500 and the second main circuit 40. The structure of the thermal management system 1 according to the embodiment of the present invention will be described in detail with reference to the accompanying drawings.

Referring to fig. 1 and 2 together, fig. 2 is a schematic diagram of pressure enthalpy corresponding to the thermal management system provided in fig. 1. In some embodiments, the first dual flow channel heat exchanger 600 may be disposed on the second branch 30, i.e., along the extending direction of the second branch 30, the first flow channel 601 is located between the first main circuit 10 and the first regulating valve 440, the first regulating valve 440 is located between the first flow channel 601 and the second heat exchanger 500, and the second flow channel 602 is located between the second heat exchanger 500 and the second port 102 of the compressor 100.

Based on the structure of the thermal management system 1, as can be seen from the pressure-enthalpy diagram shown in fig. 2, after the refrigerant in the first flow channel 601 exchanges heat with the refrigerant in the second flow channel 602, the enthalpy of the refrigerant flowing out of the outlet of the first flow channel 601 is lower than the enthalpy of the refrigerant at the inlet of the first flow channel 601, so that the first flow channel 601 can increase the supercooling degree of the refrigerant before entering the first adjusting valve 440, thereby reducing the dryness of the refrigerant at the inlet of the second heat exchanger 500, improving the heat transfer performance of the second heat exchanger 500, saving more energy, simultaneously enabling more liquid refrigerant to enter the second heat exchanger 500, improving the distribution of gas-liquid two-phase refrigerant inside the second heat exchanger 500, enabling the refrigerant flowing at the outlet of the second heat exchanger 500 to be in the gas-liquid two-phase region during the cooling process of the second heat exchanger 500, and improving the temperature uniformity of the second heat exchanger 500, thereby improving the temperature uniformity of the battery. As can be seen from fig. 2, after the heat exchange between the refrigerant in the first flow channel 601 and the refrigerant in the second flow channel 602, the enthalpy of the refrigerant flowing out of the outlet of the second flow channel 602 is higher than the enthalpy of the refrigerant at the inlet of the second flow channel 602, so that the superheat degree of the refrigerant before entering the compressor 100 can be increased by the second flow channel 602, and thus the refrigerant before entering the compressor 100 can be in a gas phase state, and when the superheat degree of the refrigerant before entering the compressor 100 is insufficient, a part of liquid-phase refrigerant enters the compressor 100 and affects the compressor 100. It should be noted that, in this document, the outlet and the inlet are directed to that when the thermal management system 1 is in the cooling mode, the port where the refrigerant flows into the valve structure or the heat exchanger structure is the inlet, and the port where the refrigerant flows out of the valve structure or the heat exchanger structure is the outlet, the valve structure includes the first regulating valve 440, the third regulating valve 420, and the second regulating valve 430, the heat exchanger structure includes the first heat exchanger 700, the second heat exchanger 500, the third heat exchanger 500, and the first dual-channel heat exchanger 600, and the port includes the port of the valve structure or the heat exchanger structure itself or the port connected to the valve structure or the heat exchanger structure, for example, in the cooling mode, the inlet of the first heat exchanger 700 is the first port 701, and the outlet of the first heat exchanger 700 is the second port 702.

Referring to fig. 3 and 4 together, fig. 4 is a schematic diagram of the pressure enthalpy corresponding to the thermal management system provided in fig. 3. In some embodiments, the first dual flow channel heat exchanger 600 is disposed on the second branch circuit 30, and the first flow channel 601 is disposed between the first regulating valve 440 and the refrigerant flow channel of the second heat exchanger 500, and the second flow channel 602 is disposed between the refrigerant flow channel of the second heat exchanger 500 and the second main circuit 40, along the extending direction of the second branch circuit 30. Based on the structure of the thermal management system 1, as can be seen from fig. 4, after the refrigerant in the first flow channel 601 exchanges heat with the refrigerant in the second flow channel 602, the enthalpy value of the refrigerant flowing out of the outlet of the first flow channel 601 is lower than the enthalpy value of the refrigerant at the inlet of the first flow channel 601, and the enthalpy value of the refrigerant flowing out of the outlet of the second flow channel 602 is higher than the enthalpy value of the refrigerant at the inlet of the second flow channel 602, so that the dryness fraction of the refrigerant at the inlet of the second heat exchanger 500 can be reduced, and further, in the refrigeration process of the second heat exchanger 500, the refrigerant flowing at the outlet of the second heat exchanger 500 is in a gas-liquid two-phase region, so that the temperature uniformity of the second heat exchanger 500 can be improved, and the temperature uniformity of the battery can be improved; meanwhile, the second flow passage 602 can increase the superheat degree of the refrigerant before entering the compressor 100, thereby increasing the service life of the compressor 100.

Referring to fig. 5 and 6 together, fig. 6 is a schematic diagram of the pressure enthalpy corresponding to the thermal management system provided in fig. 5. In some embodiments, the first runner 601 of the first dual-runner heat exchanger 600 is disposed in the first trunk 10, and the second runner 602 of the first dual-runner heat exchanger 600 is disposed in the second trunk 40. Based on the structure of the thermal management system 1, as can be seen from fig. 6, after the refrigerant in the first flow channel 601 exchanges heat with the refrigerant in the second flow channel 602, the enthalpy of the refrigerant flowing out of the outlet of the first flow channel 601 is lower than the enthalpy of the refrigerant at the inlet of the first flow channel 601, the enthalpy of the refrigerant flowing out of the outlet of the second flow channel 602 is higher than the enthalpy of the refrigerant at the inlet of the second flow channel 602, the first flow channel 601 can increase the supercooling degree of the refrigerant before entering the first regulating valve 440, and can reduce the dryness of the refrigerant at the inlet of the second heat exchanger 500, so that the refrigerant flowing through the outlet of the second heat exchanger 500 is in a gas-liquid two-phase region during the cooling process of the second heat exchanger 500, and the temperature uniformity of the second heat exchanger 500 can be improved, and the temperature uniformity of the battery can be further improved; meanwhile, the second flow passage 602 can improve the superheat degree of the refrigerant before entering the compressor 100, so that the service life of the compressor is prolonged; furthermore, the first flow channel 601 can also improve the supercooling degree of the refrigerant before entering the third regulating valve 420, improve the heat transfer performance of the third heat exchanger 310, and improve the energy saving effect.

Referring to fig. 7, 9, 11, 13 and 15 together, fig. 7 is a schematic connection block diagram of a management system according to a fourth embodiment of the present invention, fig. 9 is a schematic connection block diagram of a thermal management system 1 according to a fifth embodiment of the present invention, fig. 11 is a schematic connection block diagram of a thermal management system according to a sixth embodiment of the present invention, fig. 13 is a schematic connection block diagram of a thermal management system according to a seventh embodiment of the present invention, and fig. 15 is a schematic connection block diagram of a thermal management system according to an eighth embodiment of the present invention.

To further regulate the pressure of the refrigerant in the second heat exchanger 500, in some embodiments, the at least one throttling valve in the second thermal management unit 5000 further comprises a second regulating valve 430, in the flow direction of the working medium, the second regulating valve 430 being disposed between the refrigerant flow path of the second heat exchanger 500 and the second port 102 of the compressor 100, on the second branch 30, i.e., in the extension direction of the second branch 30, the first flow channel 601 is located between the first main line 10 and the first regulating valve 440, in the cooling mode, the first flow passage 601 is located upstream of the first regulating valve 440, or the first regulating valve 440 is located between the first flow passage 601 and the refrigerant flow passage of the second heat exchanger 500, the second flow passage 602 is located between the second heat exchanger 500 and the second regulating valve 430, in the cooling mode, the second flow passage 602 is located upstream of the second regulating valve 430 or the second flow passage 602 is disposed between the second regulating valve 430 and the second main line 40. The structure of the thermal management system 1 according to the embodiment of the present invention will be described in detail with reference to the accompanying drawings.

Referring to fig. 7 and 8 together, fig. 8 is a schematic diagram of the pressure enthalpy corresponding to the thermal management system provided in fig. 7. In some embodiments, the first flow passage 601 is disposed between the first main line 10 and the first regulation valve 440, and the second flow passage 602 is disposed between the refrigerant flow passage of the second heat exchanger 500 and the second regulation valve 430. As can be seen from fig. 8, the enthalpy of the refrigerant flowing out of the outlet of the first channel 601 is lower than that of the refrigerant at the inlet of the first channel 601, and the enthalpy of the refrigerant flowing out of the outlet of the second channel 602 is higher than that of the refrigerant at the inlet of the second channel 602, which provides the thermal management system 1 with similar advantages to the thermal management system 1 shown in fig. 1 to 6, and will not be described again.

Referring to fig. 9 and 10 together, fig. 10 is a schematic diagram of the pressure enthalpy corresponding to the thermal management system provided in fig. 9. In some embodiments, the first flow passage 601 is located on the second branch 30, the first flow passage 601 is located between the first main line 10 and the first regulating valve 440, and the second flow passage 602 is located between the second regulating valve 430 and the second main line 40, and in the cooling mode, the first flow passage 601 is located upstream of the first regulating valve 440, and the second flow passage 602 is located downstream of the second regulating valve 430. As can be seen from fig. 10, the enthalpy of the refrigerant flowing out of the outlet of the first channel 601 is lower than that of the refrigerant at the inlet of the first channel 601, and the enthalpy of the refrigerant flowing out of the outlet of the second channel 602 is higher than that of the refrigerant at the inlet of the second channel 602, which provides the thermal management system 1 with similar advantages to the thermal management system 1 shown in fig. 1 to 6, and will not be described again.

Referring to fig. 11 and 12 together, fig. 12 is a schematic diagram of the pressure enthalpy corresponding to the thermal management system provided in fig. 11. In some embodiments, the first flow passage 601 is disposed between the first main circuit 10 and the first regulating valve 440, and the second flow passage 602 is disposed between the second regulating valve 430 and the second main circuit 40, or when the first dual flow passage heat exchanger 600 is located on the second branch circuit 30, the first flow passage 601 is located upstream of the first regulating valve 440 and the second flow passage 602 is located downstream of the second regulating valve 430 in the cooling mode. As can be seen from fig. 12, the enthalpy of the refrigerant flowing out of the outlet of the first channel 601 is lower than that of the refrigerant at the inlet of the first channel 601, and the enthalpy of the refrigerant flowing out of the outlet of the second channel 602 is higher than that of the refrigerant at the inlet of the second channel 602, which provides the thermal management system 1 with similar advantages to the thermal management system 1 shown in fig. 1 to 6, and will not be described again.

Referring to fig. 13 and 14 together, fig. 14 is a pressure-enthalpy diagram for the thermal management system provided in fig. 13. In some embodiments, the first flow path 601 is disposed between the first regulating valve 440 and the first refrigerant flow path of the second heat exchanger 500, the second flow path 602 is disposed between the second regulating valve 430 and the second main line 40, or the second flow path 602 is located downstream of the second regulating valve 430. As can be seen from fig. 14, the enthalpy of the refrigerant flowing out of the outlet of the first channel 601 is lower than that of the refrigerant at the inlet of the first channel 601, and the enthalpy of the refrigerant flowing out of the outlet of the second channel 602 is higher than that of the refrigerant at the inlet of the second channel 602, and the thermal management system 1 provided by the present embodiment has the similar advantages to the thermal management system 1 shown in fig. 1 to 6, and will not be described again.

Referring to fig. 15 and 16 together, fig. 16 is a schematic diagram of the pressure enthalpy corresponding to the thermal management system provided in fig. 15. In some embodiments, the first runner 601 of the first dual-runner heat exchanger 600 is disposed in the first trunk 10, and the second runner 602 of the first dual-runner heat exchanger 600 is disposed in the second trunk 40. The thermal management system 1 according to the embodiment of the present invention has similar working principles to the thermal management system 1 shown in fig. 5, and has similar beneficial effects, which are not described again.

In some embodiments, the thermal management system 1 has a cooling mode, in which after being transmitted through the first flow passage 601, the first regulating valve 440 and the refrigerant flow passage of the second heat exchanger 500, the refrigerant at the outlet of the refrigerant flow passage of the second heat exchanger 500 can be in a gas-liquid two-phase region, and the refrigerant transmitted to the compressor 100 through the second flow passage 602 can be in a gas-phase region, that is, the superheat degree of the refrigerant at the outlet of the second flow passage 602 is greater than the superheat degree of the refrigerant at the outlet of the refrigerant flow passage of the second heat exchanger 500. Through the arrangement, the temperature uniformity of the second heat exchanger 500 can be improved, and the temperature uniformity of the battery is further improved; meanwhile, the second flow passage 602 can increase the degree of superheat of the refrigerant before entering the compressor 100, thereby increasing the life of the compressor 100.

In order to achieve the effects of throttling the pressure drop of the first regulating valve 440 and regulating the flow of refrigerant into the second heat exchanger 500, the first regulating valve 440 may alternatively be an expansion valve. In a specific implementation, the first regulating Valve 440 may be one of an Electronic Expansion Valve (EXV), a thermal Expansion Valve (TXV), an Electronic thermal Expansion Valve (ETXV) with a cut-off function, and the like.

When the first regulating valve 440 regulates the refrigerant, if the opening degree of the first regulating valve 440 is increased, the pressure loss of the refrigerant passing through the first regulating valve 440 is relatively reduced or the flow rate of the refrigerant is relatively increased, and accordingly, if the opening degree of the first regulating valve 440 is decreased, the pressure of the refrigerant flowing through the second heat exchanger 500 can be decreased or the flow rate of the refrigerant flowing through the second heat exchanger 500 can be decreased.

When the at least one throttle valve further includes the second regulating valve 430, the second regulating valve 430 is one of an expansion valve, a ball valve, and an orifice in order to enhance the regulating effect of the second regulating valve 430 on the pressure of the refrigerant flow path in the second heat exchanger 500. Specifically, the second regulating valve 430 may be one of an electronic expansion valve, a two-way ball valve, and a fixed orifice.

When the opening degree of the second adjustment valve 430 is increased when the refrigerant is adjusted by the second adjustment valve 430, the pressure loss of the refrigerant passing through the second adjustment valve 430 is relatively reduced, and the pressure difference between the refrigerant flowing through the refrigerant flow passage of the second heat exchanger 500 and the refrigerant to be sucked into the compressor 100 is relatively reduced, and at this time, the pressure of the refrigerant flowing through the second heat exchanger 500 is relatively reduced. Accordingly, if the opening degree of the first regulating valve 440 is decreased, the pressure of the refrigerant flowing through the second heat exchanger 500 can be increased.

The thermal management system 1 of the embodiment of the present invention may be applied to a single refrigeration system, and may also be applied to a heat pump system. The application of the thermal management system 1 of the embodiment of the present invention to a heat pump system will be explained below.

Referring to fig. 17 to 20 together, fig. 17 is a schematic connection block diagram of a thermal management system according to a ninth embodiment of the present invention, fig. 18 is a schematic view of a first valve device according to an embodiment of the present invention, fig. 19 is a schematic view of a refrigerant flow direction of the thermal management system shown in fig. 17 when the second heat exchanger heats, and fig. 20 is a schematic view of a refrigerant flow direction of the thermal management system shown in fig. 17 when the second heat exchanger cools. In the following, it is described that the first dual-channel heat exchanger 600 is located in the second branch 30, and the second thermal management unit 5000 may include the first dual-channel heat exchanger 600, and it is understood that the arrangement of the first dual-channel heat exchanger 600 may be the same as that shown in fig. 1 to 16, and is not described again.

In some embodiments, the at least one throttling valve further includes a second regulating valve 430, the refrigerant system may further include a first valve device 200, the first valve device 200 may be capable of switching a refrigerant flow direction of the refrigerant system, the first valve device 200 may be a four-way reversing valve, the first valve port 201 of the first valve device 200 is communicated with an outlet of the compressor 100 (the first port 101 of the compressor 100), the second valve port 202 of the first valve device 200 is communicated with an inlet of the compressor 100 (the second port 102 of the compressor 100), the first port of the first thermal management unit 300, the first port of the second thermal management unit 5000 is communicated with the third valve port 203 of the first valve device 200, the second port of the first thermal management unit 300 is capable of being communicated with the first port of the first heat exchanger 700, the second port of the second thermal management unit 5000 is communicated with the first port of the first heat exchanger 700, the second port of the first heat exchanger 700 communicates with the fourth port 204 of the first valve device 200. It will be appreciated that the first valve arrangement 200 may also be other kinds of valves or combinations of valves.

As shown in fig. 19, in the heating mode of the thermal management system 1, the outlet of the compressor 100 is communicated with the first thermal management unit 300 and the second thermal management unit 5000 through the first valve device 200, and at this time, the high-temperature and high-pressure refrigerant discharged from the compressor 100 can release heat in the first thermal management unit 300 and/or the second thermal management unit 5000, the refrigerant discharged from the first thermal management unit 300 is throttled and enters the first heat exchanger 700, the refrigerant discharged from the second thermal management unit 5000 enters the first heat exchanger 700, and the refrigerant absorbs heat in ambient air in the first heat exchanger 700 and then enters the inlet of the compressor 100 through the first valve device 200. As shown in fig. 20, in the cooling mode of the thermal management system 1, the outlet of the compressor 100 is communicated with the first heat exchanger 700 through the first valve device 200, and at this time, the high-temperature and high-pressure refrigerant discharged from the compressor 100 releases heat in the first heat exchanger 700, and the refrigerant discharged from the first heat exchanger 700 is throttled and enters the first thermal management unit 300 to absorb heat in the first thermal management unit 300, so as to reduce the temperature in the vehicle; and/or, the refrigerant discharged from the first heat exchanger 700 absorbs heat at the second thermal management unit 5000 to lower the temperature of the battery, and the refrigerant discharged from the first and second

thermal management units

300 and 5000 enters the inlet of the compressor 100 through the first valve device 200.

Alternatively, the second thermal management unit 5000 may include a first regulating valve 440, a second regulating valve 430, a second heat exchanger 500, and a first dual flow channel heat exchanger 600, in which the first dual flow channel heat exchanger 600 is located on the second branch 30 of the refrigerant transfer path, and the second heat exchanger 500 is in direct or indirect contact with the battery for regulating the temperature of the battery. Alternatively, the second heat exchanger 500 may be a direct cooling plate; the first dual-channel heat exchanger 600 has a first channel 601 and a second channel 602, both the first channel 601 and the second channel 602 are refrigerant channels, refrigerant in the first channel 601 can exchange heat with refrigerant in the second channel 602, and a second interface of the second thermal management unit 5000 communicates with the first channel 601 of the first dual-channel heat exchanger 600. The third port 203 of the first valve arrangement 200 communicates with the second flow passage 602 of the first dual flow passage heat exchanger 600 through the second regulator valve 430, wherein the first interface of the second thermal management unit 5000 is a port of the second regulator valve 430 or communicates with the port of the second regulator valve 430, as shown in FIG. 19, or the first interface of the second thermal management unit 5000 may communicate with the second flow passage 602, and the second interface of the second thermal management unit 5000 is a port of the first regulator valve 440 (as shown in FIG. 13), or communicates with the port of the first regulator valve 430, as shown in FIG. 13, or the second interface of the second thermal management unit 5000 communicates with the first flow passage 601 of the first dual flow passage heat exchanger 600, as shown in FIG. 9. In the present embodiment, the second regulating valve 430 has a function of regulating pressure and a straight-through, or the second regulating valve 430 is an expansion valve having a full opening function, and the first regulating valve 440 has a two-way throttle function.

As shown in fig. 19, in the battery heating mode, the refrigerant flow direction is: when the third port 203 of the first valve device 200, the second regulating valve 430, the second flow passage 602 of the first dual-flow-passage heat exchanger 600, the refrigerant flow passage of the second heat exchanger 500, the first regulating valve 440, the first flow passage 601 of the first dual-flow-passage heat exchanger 600, and the first port of the first heat exchanger 700 are in the fully open state, the first regulating valve 440 is in the throttle state. In the battery heating mode, since the second regulating valve 430 is fully opened and the first regulating valve 440 is throttled, the high-temperature and high-pressure refrigerant from the compressor 100 enters the second flow passage 602 of the first dual-flow-passage heat exchanger 600 and the refrigerant flow passage of the second heat exchanger 500, the refrigerant in the second heat exchanger 500 releases heat to heat the battery, the refrigerant throttled by the first regulating valve 440 enters the first flow passage 601 of the first dual-flow-passage heat exchanger 600, and since there is a temperature difference between the refrigerant in the first flow passage 601 of the first dual-flow-passage heat exchanger 600 and the refrigerant in the second flow passage 602 of the first dual-flow-passage heat exchanger 600, the refrigerant exchanges heat in the first dual-flow-passage heat exchanger 600, so that the temperature of the refrigerant entering the second heat exchanger 500 is lower than that of the refrigerant at the outlet of the compressor 100, and compared with the case that the first thermal management unit 300 is not provided with the first dual-flow-passage heat exchanger 600, the temperature difference between the outlet and the inlet side of the second heat exchanger 500 is reduced, so that the temperature of the battery is not too high, the temperature uniformity of the battery is relatively improved, and the temperature of the battery is in a reasonable range. This also relatively reduces the temperature difference between the inlet side of the second heat exchanger 500 and the outlet side of the second heat exchanger 500, improves the temperature uniformity of the second heat exchanger 500, and also makes the temperature of the battery relatively uniform. If the temperature of the battery needs to be adjusted, the heat exchange amount in the first dual-flow-channel heat exchanger 600 can be adjusted by controlling the opening degree of the second adjusting valve 430 and the opening degree of the first adjusting valve 440, so as to adjust the heat exchange amount between the battery and the second heat exchanger 500. It should be noted that "the outlet side of the second heat exchanger 500 and the inlet side of the second heat exchanger 500" described herein are defined in the case of the battery heating mode.

As shown in fig. 20, in the battery cooling mode, the flow direction of the refrigerant is: when the first port of the first heat exchanger 700, the first channel 601 of the first dual-channel heat exchanger 600, the first regulating valve 440, the second heat exchanger 500, the second channel 602 of the first dual-channel heat exchanger 600, the second regulating valve 430, and the third port 203 of the first valve device 200 are in the fully open state, the first regulating valve 440 is in the throttle state. After the refrigerant is condensed in the first heat exchanger 700, the refrigerant is further condensed in the first flow channel 601 of the first dual-flow-channel heat exchanger 600, and is throttled and depressurized by the first regulating valve 440, the refrigerant absorbs heat of the battery in the second heat exchanger 500 to reduce the temperature of the battery, and then the refrigerant enters the second flow channel 602 of the first dual-flow-channel heat exchanger 600 to exchange heat with the refrigerant in the first flow channel 601 of the first dual-flow-channel heat exchanger 600, and the first thermal management unit 300 is provided with the first dual-flow-channel heat exchanger 600, so that the temperature distribution of the refrigerant in the second heat exchanger 500 is more uniform, the temperature of the battery is more uniform, and the improvement of the performance of the battery is facilitated. If the temperature of the battery needs to be further accurately adjusted, the heat exchange amount in the first dual-flow-channel heat exchanger 600 can be adjusted by controlling the opening degree of the second adjusting valve 430 and the opening degree of the first adjusting valve 440, so as to adjust the heat exchange amount between the battery and the second heat exchanger 500.

The thermal management system 1 of the embodiment of the invention can be used in a vehicle, the first thermal management unit 300 can be arranged in an air conditioning box of the vehicle, and the second thermal management unit 5000 can regulate and control the temperature of a battery on the vehicle. In some embodiments, the refrigerant system may further include a fourth regulating valve 410, the first thermal management unit 300 includes a third heat exchanger 310 and a fourth heat exchanger 320, the third heat exchanger 310 is communicated with the fourth heat exchanger 320 through the fourth regulating valve 410, one port of the third heat exchanger 310 is a first interface of the first thermal management unit 300, one port of the fourth heat exchanger 320 is a second interface of the first thermal management unit, and the third heat exchanger 310 and the fourth heat exchanger 320 are arranged in sequence along the flow direction of the working medium. As shown in fig. 20, in the flow direction of the refrigerant, the fourth heat exchanger 320 is located upstream of the third heat exchanger 310, and in the flow direction of the refrigerant, the fourth regulating valve 410 is disposed between the third heat exchanger 310 and the fourth heat exchanger 320, a port of the third heat exchanger 310 is communicated with the third valve port 203 of the first valve device 200, that is, the port of the third heat exchanger 310 is a first interface of the first thermal management unit 300, and a port of the fourth heat exchanger 320 is communicated with a first port of the first heat exchanger 700 through the third regulating valve 420, that is, the port of the fourth heat exchanger 320 is a second interface of the first thermal management unit. Alternatively, the third regulator valve 420 may be an expansion valve.

In the present embodiment, the fourth regulator valve 410 is an expansion valve having a straight-through function, and the third regulator valve 420 has a two-way throttle function. As shown in fig. 19, in the heating mode in the vehicle interior, the flow direction of the refrigerant is: the third valve port 203, the third heat exchanger 310, the fourth regulating valve 410, the fourth heat exchanger 320 and the third regulating valve 420 of the first valve device 200 release heat from the high-temperature and high-pressure refrigerant in the third heat exchanger 310 and the fourth heat exchanger 320, the refrigerant throttled and depressurized by the third regulating valve 420 flows into the first heat exchanger 700, the refrigerant absorbs heat in the first heat exchanger 700, and the fourth regulating valve 410 is in a fully open state. As shown in fig. 20, in the cooling mode in the vehicle, the flow direction of the refrigerant is: the refrigerant throttled by the third regulating valve 420 enters the fourth heat exchanger 320 and the third heat exchanger 310 and absorbs heat, at this time, the fourth regulating valve 410 is fully opened, specifically, after the refrigerant is condensed in the first heat exchanger 700 to release heat, the refrigerant throttled and depressurized by the third regulating valve 420 flows into the fourth heat exchanger 320 and the third heat exchanger 310 and absorbs heat, and further, the temperature of the passenger compartment is reduced.

The thermal management system 1 further includes an in-vehicle heating and dehumidifying mode, and compared with the in-vehicle heating mode, in the in-vehicle heating and dehumidifying mode, the fourth regulating valve 410 is in a throttling state, and at this time, the refrigerant absorbs heat in the fourth heat exchanger 320 to reduce the temperature of the air flow of the air conditioning box, thereby reducing the humidity of the air flow, and since the third heat exchanger 310 is in the downwind direction of the fourth heat exchanger 320 and the refrigerant releases heat in the third heat exchanger 310, when the air flow passes through the third heat exchanger 310, the ambient temperature in the vehicle is increased, and the comfort level of the personnel in the vehicle is increased.

It can be appreciated that the cooling mode in the vehicle and the cooling mode of the battery can be controlled to operate simultaneously or independently by controlling the opening and closing of the respective first and

third regulating valves

440 and 420; similarly, the heating mode in the vehicle and the heating mode of the battery can be controlled to operate simultaneously or independently by controlling the opening and closing of the corresponding regulating valve.

Referring to fig. 21 to 24 together, fig. 21 is a schematic connection block diagram of a thermal management system according to a tenth embodiment of the present invention, fig. 22 is a schematic connection diagram of a thermal management system according to an eleventh embodiment of the present invention, fig. 23 is a schematic flow diagram of a refrigerant and a cooling liquid in a heat recovery mode of the thermal management system in fig. 22, and fig. 24 is a schematic flow diagram of the refrigerant and the cooling liquid in the thermal management system in fig. 22 when the second heat exchanger performs cooling and the compressor is turned on. With reference to the above possible implementation manners, the thermal management system 1 of this embodiment further includes a coolant system, where the coolant system includes a water pump 950, a fifth heat exchanger 930, and a motor temperature controller 910, where the water pump 950 is used to drive the coolant to circulate in the coolant system, the fifth heat exchanger 930 is used to release heat from the coolant to the environment, and the motor temperature controller 910 is used to exchange heat with the motor or the electronic device to control the temperature of the motor or the electronic device. The thermal management system 1 may further include a second dual-channel heat exchanger 800, where the second dual-channel heat exchanger 800 includes a first channel and a second channel, the first channel of the second dual-channel heat exchanger 800 is a refrigerant channel, the second channel of the second dual-channel heat exchanger 800 is a coolant channel, and the refrigerant in the first channel of the second dual-channel heat exchanger 800 and the coolant in the second channel of the second dual-channel heat exchanger 800 can exchange heat in the second dual-channel heat exchanger 800; in the flow direction of the working medium, the second flow passages of the first heat exchanger 700 and the second dual-flow-passage heat exchanger 800 are located between the fourth valve port 204 of the first valve device 200 and the second interface of the second thermal management unit 5000, and the coolant flow passages of the fifth heat exchanger 930 and the second dual-flow-passage heat exchanger 800, the water pump 950 and the second heat exchanger 500 are in serial communication. In the present embodiment, the fourth port 204 of the first valve device 200 communicates with the first heat exchanger 700 through the first flow channel of the second dual-flow-channel heat exchanger 800, that is, the refrigerant flowing out of the fourth port 204 of the first valve device 200 enters the first heat exchanger 700 through the first flow channel of the second dual-flow-channel heat exchanger 800.

In some embodiments, the second heat exchanger 500 also includes a first flow channel and a second flow channel, the first flow channel of the second heat exchanger 500 is a portion of a refrigerant flow channel, the second flow channel of the second heat exchanger 500 is a portion of a coolant flow channel, and the first flow channel of the second heat exchanger 500 and the second flow channel of the second heat exchanger 500 are not in communication, wherein the second flow channel of the second heat exchanger 500 is a portion of a coolant system. The connection manner of the first flow channel of the second heat exchanger 500 is as that of the second heat exchanger 500 in fig. 1 to 21, and will not be described in detail.

Referring to fig. 25, fig. 25 is a schematic structural view of the second heat exchanger shown in fig. 22. The second heat exchanger 500 includes a first connection wall 510, and the first connection wall 510 is in direct or indirect contact with the battery, where direct contact means that the first connection wall 510 is in direct contact with the battery, and indirect contact means that a heat conduction member is further provided between the first connection wall 510 and the battery. First connecting wall 510 includes first wall portions 511 and second wall portions 512, and first wall portions 511 and second wall portions 512 are alternately arranged, and along the extending direction of first connecting wall 510, one side of first wall portion 511 is one second wall portion 512, and the other side of first wall portion 511 is another second wall portion 512, and similarly, one side of second wall portion 512 is located in one first wall portion 511, and the other side of second wall portion 512 is another first wall portion 511; in a direction perpendicular to the plane of the first wall portion 511, one side of the first connecting wall 510 is a refrigerant flow passage and a coolant flow passage, and the other side of the first connecting wall 510 is a heat generating source such as a battery. Specifically, one side of first wall portion 511 is refrigerant flow channel 501 of second heat exchanger 500, the other side of first wall portion 511 is a battery, one side of second wall portion 512 is coolant flow channel 502 of second heat exchanger 500, and the other side of second wall portion 512 is a battery. It can be appreciated that the refrigerant in the second heat exchanger 500 can exchange heat with the battery, and the cooling fluid in the second heat exchanger 500 can also exchange heat with the battery. The second heat exchanger 500 comprises a cooling liquid flow passage 502 and a cooling liquid flow passage 501, both the cooling liquid and the cooling liquid of the second heat exchanger 500 can exchange heat with the battery for controlling the temperature of the battery, so that the heat management system 1 is relatively simplified, the installation space of the heat management system 1 is also reduced, the thermal inertia of the cooling liquid and the cooling liquid is different, and the temperature of the battery can be better controlled by utilizing the advantages of the two. The refrigerant and the cooling liquid in the second heat exchanger 500 may or may not exchange heat.

Referring to fig. 21 to 24, the water pump 950, the second flow channel (coolant flow channel) of the second heat exchanger 500, the motor temperature controller 910, the second flow channel of the second dual-flow-channel heat exchanger 800, and the fifth heat exchanger 930 are connected in series. The coolant system may further include a third branch 921, a fourth branch 922, a first water valve 940 and a second water valve 960, the first water valve 940 is configured to enable coolant to pass through the third branch 921 and/or the fifth heat exchanger 930, the second water valve 960 is configured to enable coolant to pass through a coolant flow passage of the fourth branch 922 and/or the second heat exchanger 500, the first water valve 940 and the second water valve 960 may be a three-way valve or a three-way proportional regulating valve, the second water valve 960 may adjust a ratio of the coolant to enter the second heat exchanger 500, each of the first water valve 940 and the second water valve 960 includes three ports, the first water valve 940 and the third branch 921 cooperate, and whether the third branch 921 bypasses the fifth heat exchanger 930 or not is selected by controlling the first water valve 940, specifically, the three ports of the first water valve 940 are respectively connected to the first port of the second flow passage of the second two-flow passage heat exchanger 800, The first port of the third branch 921 and the first port of the fifth heat exchanger 930, the second port of the third branch 921 and the second port of the fifth heat exchanger 930 are communicated with an inlet of the water pump 950.

The second water valve 960 is coupled to the fourth branch 922, and whether the fourth branch 922 bypasses the second flow path (coolant flow path) of the second heat exchanger 500 is selected by controlling the second water valve 960. Specifically, three ports of the second water valve 960 are respectively connected to an outlet of the water pump 950, a first port of the fourth branch 922, and a first port of a second flow channel of the second heat exchanger 500 to be communicated, a second port of the fourth branch 922 and a second port of the second flow channel of the second heat exchanger 500 are communicated with one port of the motor temperature controller 910, and another port of the motor temperature controller 910 is communicated with a second port of the second flow channel of the second dual-flow channel heat exchanger 800.

The operation of the thermal management system 1 in relation to the coolant system is described below, and when the vehicle is cooled, the cooling mode of the battery includes cooling with the coolant and/or cooling with the coolant, and the cooling mode of the battery is the same as that of any of the above embodiments and will not be described in detail. A cooling liquid cooling mode in the battery. The cooling liquid cooling mode of the battery includes two modes of turning on and off the compressor 100, and the operation modes of the two modes are explained in detail below.

In a first form: referring to fig. 26, fig. 26 is a schematic view illustrating a flow direction of the cooling liquid of the heat management system of fig. 22 when the second heat exchanger is cooling and the compressor is turned off. In this first form, the water pump 950 is in an on state, the compressor 100 is in an off state, and the first water valve 940 is configured to be able to close the third branch 921 and open the flow path of the fifth heat exchanger 930. Specifically, the compressor 100 is turned off, the water pump 950 is turned on, the third branch 921 is turned off by controlling the first water valve 940, and the cooling liquid circulating in the second heat exchanger 500 exchanges heat with the battery and then releases heat through the fifth heat exchanger 930 to reduce the heat of the battery, and the heat of the battery can also be released through the fifth heat exchanger 930. At this time, the fourth branch 922 may be closed by controlling the second water valve 960, the relatively low temperature coolant discharged from the fifth heat exchanger 930 may first pass through the second flow passage (coolant flow passage) of the second heat exchanger 500 and then enter the motor temperature controller 910, or the fourth branch 922 may be opened by controlling the second water valve 960, part of the coolant may enter the battery temperature controller through the fourth branch 922, and another part of the coolant may first pass through the second flow passage of the second heat exchanger 500 and then enter the motor temperature controller 910, where compared with the case where the fourth branch 922 is closed, the temperature of the motor temperature controller 910 may be relatively rapidly reduced, and if the second water valve 960 is a proportional valve, the proportion of the coolant entering the second heat exchanger 500 may also be adjusted.

In a second form, referring to fig. 24, with the compressor 100 in an open state and the third regulator valve 430 and/or the first regulator valve 440 in a closed state, the first valve apparatus 200 is configured to enable refrigerant discharged from the compressor 100 to enter the first thermal management unit 300, and the first water valve 940 is configured to enable bypassing of the fifth heat exchanger 930. When the second thermal management unit 5000 further includes the second regulating valve 430, specifically, the compressor 100 is opened, the second regulating valve 430 and/or the first regulating valve 440 are/is closed, the first valve device 200 allows the refrigerant discharged from the compressor 100 to enter the first thermal management unit 300, the refrigerant releases heat in the first thermal management unit 300, after the third regulating valve 420 is throttled, the refrigerant absorbs heat of the coolant in the second dual-channel heat exchanger 800 to reduce the temperature of the coolant, and the coolant enters the second heat exchanger 500 to reduce the temperature of the battery under the driving of the water pump 950, then the third branch 921 may bypass the fifth heat exchanger 930, and may also regulate the coolant flow channel flowing into the second heat exchanger 500 through the second water valve 960.

The heating mode of the battery includes a refrigerant heating mode, which is the same as the refrigerant heating mode shown in fig. 19 and will not be described in detail.

The thermal management system 1 further comprises a heat recovery mode, referring to fig. 23, in the in-vehicle heating mode, when the compressor 100 is in an on state, the water pump 950 is in an on state, and the first valve device 200 is configured to enable the refrigerant discharged from the compressor 100 to enter the first thermal management unit 300 and/or the second thermal management unit 5000; the first and/or

third dampers

440, 420 are opened, the first water valve 940 is configured to enable the third branch 921 to bypass the fifth heat exchanger 930, and the second water valve 960 enables the fourth branch 922 to bypass the coolant flow path of the second heat exchanger 500. Specifically, the refrigerant throttled by the third regulating valve 420 enters the first flow channels of the first heat exchanger 700 and the second dual-flow-channel heat exchanger 800, the refrigerant absorbs heat in the first heat exchanger 700, if the ambient temperature is low and the thermal management system 1 cannot absorb enough heat through the first heat exchanger 700, at this time, the water pump 950 is turned on, the second water valve 960 is controlled to open the fourth branch 922, the first water valve 940 is controlled to open the third branch 921, and the coolant absorbing heat of the motor temperature controller and/or the battery exchanges heat with the refrigerant in the second dual-flow-channel heat exchanger 800, so that heat generated by the motor is recycled. Similarly, the heat recovery mode may be operated in the battery cooling mode, or in the battery cooling mode and the vehicle interior heating mode.

It should be noted that: although the present invention has been described in detail with reference to the above-mentioned embodiments, it should be understood by those skilled in the art that the present invention may be modified and equivalents may be substituted for those skilled in the art, and all technical solutions and modifications that do not depart from the spirit and scope of the present invention should be covered by the claims of the present invention.

Claims

1. A heat management system comprises a compressor and a first heat exchanger, wherein a first port of the compressor is connected with a second port of the first heat exchanger, the heat management system is characterized by further comprising a first heat management unit, a second heat management unit and a first dual-channel heat exchanger, the first heat management unit, at least part of the second heat management unit and the first dual-channel heat exchanger are all positioned between the second port of the compressor and the first port of the first heat exchanger along the flowing direction of working media in the heat management system, the first heat management unit can exchange heat with a first heat generating source, the second heat management unit can exchange heat with a second heat generating source, the first dual-channel heat exchanger comprises a first channel and a second channel, and refrigerant in the first channel can exchange heat with refrigerant in the second channel, the second thermal management unit comprising at least one throttling valve and a second heat exchanger, the at least one throttling valve comprising a first regulating valve capable of regulating the pressure of refrigerant in the second heat exchanger,

the first regulating valve is arranged between the first heat exchanger and the second heat exchanger along the flowing direction of working media, the first flow channel is arranged between the first heat exchanger and the second heat exchanger, and the second flow channel is arranged between the second heat exchanger and the compressor.

2. The thermal management system of claim 1, comprising a first trunk, a first branch, a second branch, and a second trunk, wherein the first port of the first heat exchanger communicates with the first branch and the second branch, respectively, through the first trunk, the first branch and the second branch communicate with the second port of the compressor, respectively, through the second trunk, the first branch and the second branch are disposed in parallel with each other,

the first thermal management unit is arranged on the first branch, at least part of the second thermal management unit is arranged on the second branch, the first dual-channel heat exchanger is arranged on the second branch, or the first channel of the first dual-channel heat exchanger is arranged on the first trunk, and the second channel of the first dual-channel heat exchanger is arranged on the second trunk.

3. The thermal management system of claim 2, wherein the first dual-flow heat exchanger is disposed in the second branch,

on the second branch, the first flow passage is arranged between the first main line and the first regulating valve or between the first regulating valve and the second heat exchanger, and the second flow passage is arranged between the second heat exchanger and the second main line.

4. The thermal management system of claim 2, wherein the at least one throttling valve further comprises a second regulating valve capable of regulating a pressure of refrigerant in the second heat exchanger, in a flow direction of a working medium, the second regulating valve being disposed between the second heat exchanger and the compressor,

on the second branch, the first flow passage is arranged between the first main line and the first regulating valve, or the first flow passage is arranged between the first regulating valve and the second heat exchanger, the second flow passage is arranged between the second heat exchanger and the second regulating valve, or the second flow passage is arranged between the second regulating valve and the second main line;

or, on the second branch, the first flow channel of the first dual-flow-channel heat exchanger is disposed on the first trunk, and the second flow channel of the first dual-flow-channel heat exchanger is disposed on the second trunk.

5. The heat management system according to any of claims 1 to 4, wherein the heat management system has a cooling mode in which refrigerant at an outlet of the second heat exchanger can be in a gas-liquid two-phase region after passing through the first flow passage of the first dual-flow passage heat exchanger, the first regulating valve, and the second heat exchanger, and a superheat of refrigerant at an outlet of the second flow passage is greater than a superheat of refrigerant at an outlet of the second heat exchanger after passing through the second flow passage of the first dual-flow passage heat exchanger.

6. The thermal management system of any of claims 1-4, wherein the first regulating valve is an expansion valve, the at least one throttling valve further comprising a second regulating valve capable of regulating the pressure of the refrigerant in the second heat exchanger, the second regulating valve being one of an expansion valve, a ball valve, and a throttle orifice.

7. The thermal management system of any of claims 1-4, wherein at least one of said throttling valves further comprises a second regulating valve, the thermal management system further includes a first valve device capable of switching a refrigerant flow direction of the refrigerant system and a third regulating valve, the first port of the compressor is in communication with the first port of the first valve device, the first interface of the first thermal management unit and the first interface of the second thermal management unit are in communication with the third port of the first valve device, the second interface of the first thermal management unit is communicated with the first port of the first heat exchanger through the third regulating valve, the second port of the second thermal management unit is communicated with the first port of the first heat exchanger, and the second port of the first heat exchanger is communicated with the fourth port of the first valve device;

the first interface of the second thermal management unit is a port of the second regulating valve, or is communicated with a second flow passage of the first dual-flow-passage heat exchanger, and the second interface of the second thermal management unit is a port of the first regulating valve, or is communicated with the first flow passage of the first dual-flow-passage heat exchanger.

8. The thermal management system according to claim 7, wherein the thermal management system is applied to a vehicle, the first thermal management unit is arranged in an air conditioning box of the vehicle, and the second thermal management unit can regulate and control the temperature of a vehicle battery;

the first heat management unit further comprises a fourth regulating valve, a third heat exchanger and a fourth heat exchanger, the third heat exchanger is communicated with the fourth heat exchanger through the fourth regulating valve, one port of the third heat exchanger is a first interface of the first heat management unit, one port of the fourth heat exchanger is a second interface of the first heat management unit, and the third heat exchanger and the fourth heat exchanger are arranged along the flowing direction of the refrigerant.

9. The thermal management system of claim 7, applied to a vehicle, further comprising a coolant system, the second heat exchanger having a refrigerant flow path and a coolant flow path, the coolant system including the coolant flow path of the second heat exchanger, the refrigerant flow path and the coolant flow path of the second heat exchanger not being in communication;

the second heat exchanger comprises a first connecting wall, the first connecting wall is in direct or indirect contact with a heat generating source to perform heat exchange, the first connecting wall comprises a first wall portion and a second wall portion, the first wall portion and the second wall portion are alternately arranged along the extending direction of the first connecting portion, the plane direction perpendicular to the first connecting wall is along, one side of the first wall portion is a refrigerant flow channel, the other side of the first wall portion is the heat generating source, one side of the second wall portion is a cooling liquid flow channel, and the other side of the second wall portion is the heat generating source.

10. The thermal management system of claim 9, further comprising a second dual flow channel heat exchanger having a refrigerant flow channel and a coolant flow channel, the coolant system further comprising a water pump, a fifth heat exchanger, the coolant flow channel of the second dual flow channel heat exchanger, and the coolant flow channel of the second heat exchanger;

along the flowing direction of the working medium, the refrigerant flow channels of the first heat exchanger and the second dual-flow-channel heat exchanger are arranged between the fourth valve port of the first valve device and the second interface of the second thermal management unit, and the coolant flow channels of the fifth heat exchanger and the second dual-flow-channel heat exchanger, the water pump and the coolant flow channel of the second heat exchanger are communicated in series.

11. The thermal management system of claim 10, wherein the coolant system further comprises a third branch, a first water valve, a fourth branch, and a second water valve, the first water valve configured to enable coolant to pass through the third branch and/or the fifth heat exchanger, the second water valve configured to enable coolant to pass through a coolant flow path of the fourth branch and/or the second heat exchanger;

the cooling liquid system also comprises a motor temperature controller, and the motor temperature controller is serially arranged with the cooling liquid flow passage of the second dual-flow-passage heat exchanger;

the heat management system further comprises a heat recovery mode, wherein in the heat recovery mode, the compressor is in an open state, the water pump is in an open state, the first valve device is configured to enable refrigerant discharged by the compressor to enter the first heat management unit and/or the second heat management unit, the first regulating valve and/or the third regulating valve is opened, the first water valve is configured to enable the third branch to bypass the fifth heat exchanger, and the second water valve enables the fourth branch to bypass the second heat exchanger.

12. The thermal management system of claim 11, wherein said thermal management system comprises a coolant cooling mode;

in the cooling liquid cooling mode, the water pump is in an on state, the compressor is in an off state, and the first water valve is configured to close the third branch and open a flow path of the fifth heat exchanger; alternatively, in the cooling liquid cooling mode, the compressor is in an open state and the first regulator valve is in a closed state, the first valve arrangement is configured to enable refrigerant discharged by the compressor to enter the first thermal management unit, and the first water valve is configured to enable bypassing of the fifth heat exchanger.

13. The thermal management system of claim 12, wherein the second water valve is a proportional regulating valve, the second water valve being capable of regulating a proportion of coolant entering the second heat exchanger.