Thermal management system comprising cooling and heating dual-purpose heat exchanger

Abstract

The utility model discloses a heat management system containing a cooling and heating dual-purpose heat exchanger, which comprises a cooling and heating dual-purpose plate heat exchanger, a battery pack liquid inlet on the cooling and heating dual-purpose plate heat exchanger is communicated with an outlet of a power battery through a guide pipe, and a battery pack liquid outlet on the cooling and heating dual-purpose plate heat exchanger is connected with an inlet of a three-way guide pipe. Two outlets of the three-way guide pipe are connected with an inlet of the expansion kettle and an inlet of the battery pump respectively, an outlet of the expansion kettle is connected with an inlet of the battery pump through a guide pipe, and an outlet of the battery pump is connected with an inlet of the water heating heater through a guide pipe. A double-source heat pump of an air source and a water source of a passenger compartment is achieved, electric control waste heat of a motor is effectively utilized to heat a power battery, the mode requirement of a heat pump heat management system is met, heating power consumption in a low-temperature environment is reduced, the number of system parts is small, cost is low, the development difficulty of a controller is small, and application and popularization of the heat pump heat management system are facilitated.

Description

TECHNICAL FIELD

[0001] The utility model relates to new energy automobile heat pump air conditioning system technical field, concretely is a kind of heat management system containing cold and warm dual-purpose heat exchanger. BACKGROUND

[0002] In the field of new energy vehicles, the problem of increased energy consumption and decreased range after starting heating in winter has been the main pain point of users. With the continuous development of technology, the heat management system based on heat pump technology has gradually emerged and been widely used. To solve this problem, the existing system structure is complex, the air source and water source of the passenger cabin are heated and cooled separately, and the waste heat of battery heating and cooling cannot be recycled, so a large amount of electric energy is consumed, which is not convenient to use. UTILITY MODEL CONTENT

[0003] The utility model solves the technical problem of overcoming the defects of the prior art and provides a heat management system containing a cold and warm dual-purpose heat exchanger. By using a cold and warm dual-purpose parallel flow heat exchanger and a cold and hot dual-purpose plate heat exchanger, a dual-source heat pump for the air source and water source of the passenger cabin is realized, the motor electric control waste heat is effectively utilized to heat the power battery, the mode requirement of the heat pump heat management system is met, the heating power consumption in low temperature environment is reduced, the number of system components is small, the cost is low, the controller development difficulty is small, and the heat pump heat management system is conducive to popularization and application, which can effectively solve the problems in the background technology.

[0004] In order to achieve the above object, the utility model provides the following technical scheme: a heat management system containing cold and warm dual -purpose heat exchanger, including cold and warm dual -purpose plate type heat exchanger, the battery pack liquid import on cold and warm dual -purpose plate type heat exchanger passes through the pipe and the outlet of power battery intercommunication, and the battery pack liquid export on cold and warm dual -purpose plate type heat exchanger is connected with the import of three -way pipe, and the two exports of this three -way pipe are connected with the import of expansion kettle and the import of battery pump respectively, the export of expansion kettle is connected with the import of battery pump through the pipe, and the export of battery pump is connected with the import of water heating heater through the pipe, the export of water heating heater is connected with the import of power battery through the pipe, and the PTC water inlet and PTC water outlet of cold and warm dual -purpose plate type heat exchanger are connected with motor cold control system, and the refrigerant export of cold and warm dual -purpose plate type heat exchanger is connected with the import of gas -liquid separator through the pipe, the export of gas -liquid separator is connected with the import of compressor through the pipe, the export of compressor is connected with the import of electromagnetic valve no.

[0005] Further, one side of the heat pump heat exchanger is provided with a front end fan, and the front end fan blows air to the low-temperature radiator on the heat pump heat exchanger and the motor cooling control system.

[0006] Further, the motor cooling control system includes a low-temperature radiator, the inlet of the low-temperature radiator is connected with the second port of a three-way valve through a pipe, the first port of the three-way valve is connected with the cold and warm dual-purpose plate heat exchanger, the third port of the three-way valve is connected with the outlet of the motor electric control through a pipe, the inlet of the motor electric control is connected with the outlet of the electric drive pump through a pipe, the inlet of the electric drive pump is connected with the outlet of the low-temperature radiator, and the inlet of the electric drive pump and the low-temperature radiator are further connected in parallel with an expansion kettle two.

[0007] Further, the low-temperature radiator, the heat pump heat exchanger, and the front end fan are arranged in sequence from left to right.

[0008] Compared with the prior art, the heat management system with the cold and warm dual-purpose heat exchanger has the advantages that: the structure is simple, the operation is simple, the motor electric control waste heat is transferred to the power battery loop and the passenger cabin, heating of the power battery and the passenger cabin is realized, low-temperature environment heating energy consumption is reduced, winter cruising range is improved, the air source and the water source of the passenger cabin are realized by a cold and warm dual-purpose parallel flow heat exchanger and a cold and hot dual-purpose plate heat exchanger, double-source heat pump, the motor electric control waste heat is effectively utilized to heat the power battery, the mode requirement of the heat pump heat management system is met, the heating power consumption of the low-temperature environment is reduced, the number of system parts is small, the cost is low, the controller development difficulty is small, and the heat pump heat management system is conducive to popularization and application. BRIEF DESCRIPTION OF DRAWINGS

[0009] Figure 1 It is a structure schematic view of the utility model;

[0010] Figure 2 It is a structure schematic view of the utility model passenger cabin refrigeration mode;

[0011] Figure 3 It is a structure schematic view of the utility model battery refrigeration mode;

[0012] Figure 4 It is a structure schematic view of the utility model passenger cabin and battery refrigeration mode;

[0013] Figure 5 It is a structure schematic view of the utility model passenger cabin air source heat pump heating mode;

[0014] Figure 6 It is a structure schematic view of the utility model passenger cabin water source heat pump heating mode;

[0015] Figure 7 It is a structure schematic view of the utility model passenger cabin small circulation dehumidification mode;

[0016] Figure 8 It is a structure schematic view of the utility model passenger cabin low-temperature dehumidification mode;

[0017] Figure 9 It is a structure schematic view of the utility model passenger cabin high-temperature dehumidification mode;

[0018] Figure 10 It is a structure schematic view of the utility model passenger cabin dehumidification + battery refrigeration mode.

[0019] In the figure: 1 cold and warm plate heat exchanger, 2 power battery, 3 expansion kettle, 4 battery pump, 5 water heating heater, 6 gas-liquid separator, 7 compressor, 8 electromagnetic valve one, 9 heat pump heat exchanger, 11 electromagnetic valve two, 12 electromagnetic valve three, 13 cold and warm parallel flow heat exchanger, 14 electromagnetic valve four, 15 large-diameter electronic expansion valve two, 16 large-diameter electronic expansion valve one, 17 electromagnetic valve five, 18 front-end fan, 19 low-temperature radiator, 20 three-way valve, 21 motor electric control, 22 electric drive pump, 23 motor electric control, 24 throttle valve. DETAILED DESCRIPTION

[0020] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0021] Please refer to Figures 1-10The utility model provides a technical scheme: a kind of heat management system containing cold and warm dual-purpose heat exchanger, including cold and warm dual-purpose plate heat exchanger 1, the battery pack liquid import on cold and warm dual-purpose plate heat exchanger 1 is communicated with the outlet of power battery 2 by conduit, and the battery pack liquid export on cold and warm dual-purpose plate heat exchanger 1 is connected with the import of three-way conduit, two exports of this three-way conduit are connected with respectively the import of expansion kettle 3 and the import of battery pump 4, the export of expansion kettle 3 is connected with the import of battery pump 4 by conduit, and the export of battery pump 4 is connected with the import of water heating heater 5 by conduit, the export of water heating heater 5 is communicated with the import of power battery 2 by conduit, and the PTC water inlet and PTC water outlet of cold and warm dual-purpose plate heat exchanger 1 are communicated with motor cold control system, and the refrigerant export of cold and warm dual-purpose plate heat exchanger 1 is connected with the import of gas-liquid separator 6 by conduit, the export of gas-liquid separator 6 is connected with the import of compressor 7 by conduit, the export of compressor 7 is connected with the import of solenoid valve one 8, the export of solenoid valve one 8 is connected with the first port of heat pump heat exchanger 9 by conduit, the export of compressor 7 is also connected with the import of solenoid valve two 11 by conduit, the export of solenoid valve two 11 is communicated with the export of solenoid valve three 12 and the first import of cold and warm dual-purpose parallel flow heat exchanger 13 respectively by three-way conduit, the export of solenoid valve three 12 is communicated with the second import of cold and warm dual-purpose parallel flow heat exchanger 13, and the second import of cold and warm dual-purpose parallel flow heat exchanger 13 is communicated with the refrigerant export of cold and warm dual-purpose plate heat exchanger 1 by solenoid valve four 14, cold and warm dual-purpose parallel flow heat exchanger 13 is prior art, for example, realize motor electric control waste heat to be transferred to power battery loop and passenger compartment in the patent with patent authorized announcement No. CN215447537U, complete heating to power battery and passenger compartment, reduce low-temperature environment heating energy consumption, improve winter range, the export of solenoid valve two 11 is communicated with the export of solenoid valve three 12 and the first import of cold and warm dual-purpose parallel flow heat exchanger 13 respectively by three-way conduit, the export of solenoid valve three 12 is communicated with the second import of cold and warm dual-purpose parallel flow heat exchanger 13, and the second import of cold and warm dual-purpose parallel flow heat exchanger 13 is communicated with the refrigerant export of cold and warm dual-purpose plate heat exchanger 1 by solenoid valve four 14, cold and warm dual-purpose parallel flow heat exchanger 13 is prior art, for example, realize motor electric control waste heat to be transferred to power battery loop and passenger compartment in the patent with patent authorized announcement No. CN215447537U, complete heating to power battery and passenger compartment, reduce low-temperature environment heating energy consumption, improve winter range, the third port and the fourth port of cold and warm dual-purpose parallel flow heat exchanger 13 are communicated with the port of large-diameter electronic expansion valve two 15 and large-diameter electronic expansion valve one 16 respectively, and large-diameter electronic expansion valve two 15 and large-diameter electronic expansion valve one 16 are communicated with the second port of heat pump heat exchanger 9, the first port of heat pump heat exchanger 9 is communicated with the import of gas-liquid separator 6 by solenoid valve five 17, and the second port of heat pump heat exchanger 9 is also communicated with the refrigerant import of cold and warm dual-purpose plate heat exchanger 1,Furthermore, a throttling valve 24 is installed on the connecting conduit between the heat pump heat exchanger 9 and the dual-purpose heat exchanger 1. A front-end fan 18 is installed on one side of the heat pump heat exchanger 9, which blows heat to the heat pump heat exchanger 9 and the low-temperature radiator 19 on the motor refrigeration system. The motor refrigeration system includes the low-temperature radiator 19. The inlet of the low-temperature radiator 19 is connected to the second port of a three-way valve 20 through a conduit. The first port of the three-way valve 20 is connected to the dual-purpose heat exchanger 1. The third port of the three-way valve 20 is connected to the outlet of the motor control unit 21 through a conduit. The inlet of the motor control unit 21 is connected to the outlet of the electric pump 22 through a conduit. The inlet of the electric pump 22 is connected to the outlet of the low-temperature radiator 19, and the inlet of the electric pump 22 is also connected in parallel with the low-temperature radiator 19. The thermal management system, comprising an expansion tank 23, a low-temperature radiator 19, a heat pump heat exchanger 9, and a front-end fan 18 arranged from left to right, features a simple structure and easy operation. It transfers waste heat from the motor and electronic control system to the power battery circuit and passenger compartment, heating these components and reducing energy consumption in low-temperature environments, thus extending winter driving range. Through a dual-source heat pump system (air and water source) using both a parallel-flow heat exchanger and a plate heat exchanger, it effectively utilizes waste heat from the motor and electronic control system to heat the power battery, meeting the requirements of the heat pump thermal management system. This reduces power consumption in low-temperature environments, minimizes the number of system components, lowers costs, and simplifies controller development, facilitating the widespread application of heat pump thermal management systems.

[0022] When in use: In the first crew cabin cooling mode, such as Figure 2 As shown, in this mode, the motor cooling control system operates, and the electric drive pump 22 operates to draw water from the expansion tank 23 and then into the motor control unit 21 to cool it. The cooled water then enters the low-temperature radiator 19, where the front fan 18 blows air to cool the water. Meanwhile, solenoid valves 1-8, 3-12, and 4-14 are opened, while solenoid valves 2-11 and 5-17 are closed. The refrigerant is compressed from the compressor 7 and enters the heat pump heat exchanger 9 through solenoid valve 1-8 to release heat. After being throttled by the large-diameter electronic expansion valve 2-15 and the large-diameter electronic expansion valve 1-16, it enters the dual-purpose parallel flow heat exchanger 13 to evaporate and absorb heat, thus cooling the passenger cabin. Finally, it enters the gas-liquid separator 6 and the compressor 7 through solenoid valves 3-12 and 4-14 to complete the refrigeration cycle.

[0023] Second battery cooling mode, such as Figure 3As shown, in this mode, the solenoid valve 8 for heat dissipation in the electric drive circuit is open, while solenoid valves 11, 17, 12, and 14 are closed, and large-diameter electronic expansion valves 15 and 16 are closed. After being compressed by the compressor 7, the refrigerant enters the heat pump heat exchanger 9 through the solenoid valve 8 to release heat. After being throttled by the throttling valve 24, it enters the dual-purpose cooling and heating plate heat exchanger 1 to evaporate and absorb heat, thus cooling the battery circuit. After that, it enters the gas-liquid separator 6 and the compressor 7 to complete the refrigeration cycle.

[0024] The third crew cabin and battery are cooled simultaneously, such as Figure 4 As shown, in this mode, the electric drive circuit dissipates heat. Solenoid valves 1-8, 3-12, and 4-14 are open, while solenoid valves 2-11 and 5-17 are closed. After being compressed by compressor 7, the refrigerant enters heat pump heat exchanger 9 through solenoid valve 1-8 to release heat. After being throttled by large-diameter electronic expansion valve 2-15 and large-diameter electronic expansion valve 1-16, it enters parallel flow heat exchanger 13 for both heating and cooling to evaporate and absorb heat, thus cooling the passenger cabin. After being throttled by solenoid valves 3-12 and 4-14, it enters gas-liquid separator 6. After being throttled by throttling valve 24, it enters plate heat exchanger 1 for both heating and cooling to evaporate and absorb heat, thus cooling the battery circuit. Finally, it enters gas-liquid separator 6 to complete the refrigeration cycle.

[0025] The fourth crew cabin uses an air-source heat pump heating mode, such as... Figure 5 As shown, solenoid valve 18 and solenoid valve 414 are closed, while solenoid valve 21, solenoid valve 312 and solenoid valve 517 are open. After the refrigerant is compressed from the compressor 7, it enters the dual-purpose parallel flow heat exchanger 13 through solenoid valve 21 and solenoid valve 312 to condense and release heat, thus heating the passenger cabin. After being throttled by large-diameter electronic expansion valve 215 and large-diameter electronic expansion valve 16, it enters the heat pump heat exchanger 9 to absorb heat from the air. Then, it enters the gas-liquid separator 6 and the compressor 7 through solenoid valve 517, completing the heating cycle of the air source heat pump.

[0026] The fifth crew cabin uses a water source heat pump heating mode; such as Figure 6 As shown, solenoid valve 18, solenoid valve 414 and solenoid valve 517 are closed, and solenoid valve 21 and solenoid valve 312 are open. After the refrigerant is compressed from the compressor 4, it enters the dual-purpose parallel flow heat exchanger 13 through solenoid valve 21 and solenoid valve 312 to condense and release heat, thereby heating the passenger cabin. After passing through the large-diameter electronic expansion valve 15 for throttling, it enters the dual-purpose plate heat exchanger 1 to absorb heat from the battery electric drive, and then enters the gas-liquid separator 6 and the compressor 7 to complete the heating cycle of the air source heat pump.

[0027] If the ambient temperature is low, the heat pump heat exchanger 9 will have a poor heat absorption effect from the air, and the heating mode can be switched to water source heat pump mode. If the coolant temperature in the battery electric drive circuit is low in water source heat pump mode, the water heater 5 in the battery circuit can be turned on to supplement heat. When the air source heat pump mode cannot operate and the water source heat pump has a small heating capacity, the heater in the cooling and heating parallel flow heat exchanger 13 can be turned on to supplement heat and meet the needs of defrosting, defogging, and heating in the passenger compartment. When the air source or water source heat pump meets the heat load requirements of the passenger compartment, the water heater 5 is turned off. The cooling and heating parallel flow heat exchanger 13 and the heat pump heat exchanger 9 have opposite flow directions in the cooling and heating cycles, which is conducive to giving full play to the heat exchange capacity of the heat exchanger and improving the energy efficiency ratio of the system.

[0028] The sixth crew cabin uses a small-circulation dehumidification mode, such as... Figure 7 As shown, solenoid valve 1 (8), solenoid valve 3 (12), and solenoid valve 5 (17) are closed, while solenoid valve 2 (11) and solenoid valve 4 (14) are open. After being compressed by compressor 6, the refrigerant enters the dual-purpose parallel flow heat exchanger 13 through solenoid valve 2 (11), flows through the fully open large-diameter electronic expansion valve 2 (15) and the throttling large-diameter electronic expansion valve 1 (16), and then through the dual-purpose parallel flow heat exchanger 13, it enters the gas-liquid separator 6 and compressor 7 through solenoid valve 4 (14), completing the dehumidification cycle.

[0029] The seventh crew cabin's low-temperature dehumidification mode, such as Figure 8 As shown, in the low-temperature dehumidification mode of the crew cabin, solenoid valves 1-8, 3-12, and 5-17 are closed, while solenoid valves 2-11 and 4-14 are open. After being compressed by compressor 7, the refrigerant enters the dual-purpose parallel flow heat exchanger 13 through solenoid valve 2-11, flows through the fully open large-diameter electronic expansion valve 2-15, one path is throttled by large-diameter electronic expansion valve 1-16 and then enters the dual-purpose parallel flow heat exchanger 13, while the other path is throttled by throttling valve 24 and then enters the dual-purpose plate heat exchanger 1. The two paths merge and enter the gas-liquid separator 6 and compressor 7, completing the dehumidification cycle.

[0030] The eighth crew cabin's high-temperature dehumidification mode, such as Figure 9 As shown, in the high-temperature dehumidification mode of the passenger cabin, solenoid valves 12 and 17 are closed, while solenoid valves 8, 11, and 14 are open. Refrigerant, after being compressed by compressor 7, flows through solenoid valve 8 and heat pump heat exchanger 9 to large-diameter electronic expansion valve 16, and through solenoid valve 11 into the dual-purpose (heating and cooling) parallel flow heat exchanger 13. It then flows through the fully open large-diameter electronic expansion valve 15 to large-diameter electronic expansion valve 16. The two flows converge at large-diameter electronic expansion valve 16 and are throttled before entering the dual-purpose (heating and cooling) parallel flow heat exchanger 13. Finally, they pass through solenoid valve 14 into gas-liquid separator 6 and compressor 7, completing the dehumidification cycle.

[0031] The ninth crew cabin features dehumidification and battery cooling modes; such as... Figure 10As shown; Solenoid valves 3-12 and 5-17 are closed, while solenoid valves 1-8, 2-11, and 4-14 are open. After being compressed by compressor 7, the refrigerant flows through solenoid valve 1-8 and heat pump heat exchanger 9 to large-diameter electronic expansion valves 2-15 and 1-16. Another path flows through solenoid valve 2-11 into the dual-purpose parallel flow heat exchanger 13. The refrigerant then flows through the fully open large-diameter electronic expansion valve 2-15 to large-diameter electronic expansion valve 1-16 and throttle valve 24. After being throttled by large-diameter electronic expansion valve 1-16, it enters the dual-purpose parallel flow heat exchanger 13. It then flows through solenoid valve 4-14 into gas-liquid separator 6 and compressor 7. After being throttled by throttle valve 24, it enters the dual-purpose plate heat exchanger 1 and then enters gas-liquid separator 6 and compressor 7 to complete the cabin dehumidification and battery cooling cycle.

[0032] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention.

Claims

1. A thermal management system containing a dual-purpose (heating and cooling) heat exchanger, comprising a dual-purpose (heating and cooling) plate heat exchanger (1), characterized in that: The battery pack electrolyte inlet of the dual-purpose heat exchanger (1) is connected to the outlet of the power battery (2) via a conduit, while the battery pack electrolyte outlet of the dual-purpose heat exchanger (1) is connected to the inlet of a three-way conduit. The two outlets of the three-way conduit are respectively connected to the inlet of the expansion tank (3) and the inlet of the battery pump (4). The outlet of the expansion tank (3) is connected to the inlet of the battery pump (4) via a conduit, while the outlet of the battery pump (4) is connected to the inlet of the water heater (5) via a conduit. The outlet of the water heater (5) is connected to the power battery via a conduit. (2) The inlet of the heat exchanger (1) is connected to the PTC inlet and outlet of the heat exchanger (1), which is used for both heating and cooling. The refrigerant outlet of the heat exchanger (1) is connected to the inlet of the gas-liquid separator (6) through a conduit. The outlet of the gas-liquid separator (6) is connected to the inlet of the compressor (7) through a conduit. The outlet of the compressor (7) is connected to the inlet of the solenoid valve (8). The outlet of the solenoid valve (8) is connected to the first port of the heat pump heat exchanger (9) through a conduit. The outlet of the compressor (7) is also connected to the second solenoid valve (9) through a conduit. The inlet connection of solenoid valve 11) is made, and the outlet of solenoid valve 2 (11) is connected to the outlet of solenoid valve 3 (12) and the first port of the dual-purpose parallel flow heat exchanger (13) via a three-way conduit. The outlet of solenoid valve 3 (12) is connected to the second port of the dual-purpose parallel flow heat exchanger (13). The second port of the dual-purpose parallel flow heat exchanger (13) is connected to the refrigerant outlet of the dual-purpose plate heat exchanger (1) via solenoid valve 4 (14). The third and fourth ports of the dual-purpose parallel flow heat exchanger (13) are connected to the large-diameter electronic expansion valve. The ports of expansion valve 2 (15) and large-diameter electronic expansion valve 1 (16) are connected. Both large-diameter electronic expansion valve 2 (15) and large-diameter electronic expansion valve 1 (16) are connected to the second port of heat pump heat exchanger (9). The first port of heat pump heat exchanger (9) is connected to the inlet of gas-liquid separator (6) through solenoid valve 5 (17). The second port of heat pump heat exchanger (9) is also connected to the refrigerant inlet of cooling and heating plate heat exchanger (1). A throttling valve (24) is provided on the connecting pipe between heat pump heat exchanger (9) and cooling and heating plate heat exchanger (1).

2. A thermal management system containing a dual-purpose heating and cooling heat exchanger according to claim 1, characterized in that: A front-end fan (18) is provided on one side of the heat pump heat exchanger (9), and the front-end fan (18) blows heat to the heat pump heat exchanger (9) and the low-temperature radiator (19) on the motor cooling system.

3. A thermal management system containing a dual-purpose heating and cooling heat exchanger according to claim 1, characterized in that: The motor cooling control system includes a low-temperature radiator (19). The inlet of the low-temperature radiator (19) is connected to the second port of a three-way valve (20) through a conduit. The first port of the three-way valve (20) is connected to a heat exchanger (1) for both heating and cooling. The third port of the three-way valve (20) is connected to the outlet of a motor control unit (21) through a conduit. The inlet of the motor control unit (21) is connected to the outlet of an electric pump (22) through a conduit. The inlet of the electric pump (22) is connected to the outlet of the low-temperature radiator (19). An expansion tank (23) is also connected in parallel between the inlet of the electric pump (22) and the low-temperature radiator (19).

4. A thermal management system containing a dual-purpose heating and cooling heat exchanger according to claim 3, characterized in that: The low-temperature radiator (19), heat pump heat exchanger (9), and front-end fan (18) are arranged from left to right.

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