CN116215176A - Direct heat pump automobile air conditioning system for waste heat gradient recovery - Google Patents

Direct heat pump automobile air conditioning system for waste heat gradient recovery Download PDF

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Publication number
CN116215176A
CN116215176A CN202310287802.4A CN202310287802A CN116215176A CN 116215176 A CN116215176 A CN 116215176A CN 202310287802 A CN202310287802 A CN 202310287802A CN 116215176 A CN116215176 A CN 116215176A
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China
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way valve
heat
vehicle
heat exchanger
battery
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CN202310287802.4A
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Chinese (zh)
Inventor
李明
吕然
李晓桐
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Jilin University
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Jilin University
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Priority to CN202310287802.4A priority Critical patent/CN116215176A/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00357—Air-conditioning arrangements specially adapted for particular vehicles
    • B60H1/00385—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell
    • B60H1/00392—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell for electric vehicles having only electric drive means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
    • B60H1/03—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant and from a source other than the propulsion plant
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
    • B60H1/14—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant otherwise than from cooling liquid of the plant, e.g. heat from the grease oil, the brakes, the transmission unit
    • B60H1/143—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant otherwise than from cooling liquid of the plant, e.g. heat from the grease oil, the brakes, the transmission unit the heat being derived from cooling an electric component, e.g. electric motors, electric circuits, fuel cells or batteries
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60S—SERVICING, CLEANING, REPAIRING, SUPPORTING, LIFTING, OR MANOEUVRING OF VEHICLES, NOT OTHERWISE PROVIDED FOR
    • B60S1/00—Cleaning of vehicles
    • B60S1/02—Cleaning windscreens, windows or optical devices
    • B60S1/023—Cleaning windscreens, windows or optical devices including defroster or demisting means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

The invention is suitable for the technical field of automobile air conditioners, and particularly relates to a direct heat pump automobile air conditioning system capable of recovering waste heat in steps. And in-vehicle heating is carried out by using the waste heat of the motor as a low-temperature heat source under the low-temperature condition, so that the problems that the exhaust temperature of the compressor is too high, the heating quantity is obviously insufficient and the like when the heat pump type automobile air conditioner runs under the low-temperature working condition are solved. And dehumidification can be performed during refrigeration, so that the internal thermal comfort of the vehicle is improved.

Description

Direct heat pump automobile air conditioning system for waste heat gradient recovery
Technical Field
The invention belongs to the technical field of automobile air conditioners, and particularly relates to a direct heat pump automobile air conditioning system for waste heat cascade recovery.
Background
In the field of automobiles, in order to reduce environmental pollution, large-scale development of electric automobiles has become a trend, and realization of large-scale application of new energy automobiles while comprehensively improving the quality and performance of the whole electric automobiles is one of the main stream directions of current development.
The pure electric vehicle is not provided with the fuel engine, the air conditioning system of the vehicle can not be driven by the engine directly except the compressor, heating in winter can not be carried out continuously by utilizing the waste heat of the engine, the prior electric vehicle is mainly provided with the PTC electric heater for heating directly, the efficiency is low, the endurance mileage of the electric vehicle is obviously reduced, and the energy conservation and emission reduction targets are not met in the long term.
Disclosure of Invention
The embodiment of the invention aims to provide a direct heat pump automobile air conditioning system for waste heat gradient recovery, which aims to solve the problems that the conventional electric automobile is directly heated by a PTC electric heater, the efficiency is low, and the endurance mileage of the electric automobile is remarkably reduced.
The embodiment of the invention is realized in such a way that a direct heat pump automobile air conditioning system for waste heat cascade recovery comprises: the waste heat temperature control circulation module, PTC heater (10), refrigerant circulation module, heat exchange module and battery temperature control module in the car, refrigerant circulation module is connected with outer heat exchanger (15) of car through cross valve (14), outer heat exchanger (15) is connected with heat exchange module and battery temperature control module in the car through the three-way valve of taking two-way electronic expansion valve, refrigerant circulation module passes through cross valve (14) and is connected with heat exchange module and battery temperature control module in the car, PTC heater (10) are installed in waste heat temperature control circulation module, waste heat temperature control circulation module is connected with battery temperature control module.
Preferably, the waste heat temperature control circulation module comprises a first water pump (1), a proportion five-way valve (6), an in-vehicle radiator (11), a motor radiator (7) and a motor radiator fan (8), wherein the first water pump (1) passes through a charging system (2), a direct current power supply converter (3), a motor control system (4) and a motor (5) through a pipeline, and is connected with the proportion five-way valve (6), one end of the motor radiator (7) is connected with the proportion five-way valve (6), the other end of the motor radiator is connected with a first electromagnetic three-way valve (9), the motor radiator fan (8) is arranged on one side of the motor radiator (7), one end of a PTC heater (10) is connected with the proportion five-way valve (6), the other end of the PTC heater (1) is connected with the first water pump (1), one end of the in-vehicle radiator (11) is connected with the proportion five-way valve (6), the other end of the PTC heater is connected with the first electromagnetic three-way valve (9), and the proportion five-way valve (6) and the first electromagnetic three-way valve (9) are connected with the first electromagnetic three-way valve (26), and the expansion pot is connected with the first water pump (1).
Preferably, the refrigerant circulation module comprises a compressor (13) and a gas-liquid separator (19), one end of the compressor (13) is connected with the gas-liquid separator (19), the other end of the compressor is connected with the four-way valve (14), and the gas-liquid separator (19) is also connected with the four-way valve (14).
Preferably, the heat exchange module in the car includes heat exchanger (17) in the first car, radiator fan (18) and second car in heat exchanger (28), and one end of heat exchanger (17) is connected with proportion five-way valve (6) in the first car, and the other end is connected with second electromagnetism three-way valve (27), and two ports of second electromagnetism three-way valve (27) are connected with the both ends of heat exchanger (28) in the second car, and second electromagnetism three-way valve (27) still communicates with cross valve (14) and battery temperature control module.
Preferably, 5, a direct heat pump automobile air conditioning system for waste heat cascade recovery according to claim 2, which is characterized in that
Preferably, the direct heat pump automobile air conditioning system with the waste heat step recovery comprises an in-automobile refrigeration mode, an in-automobile refrigeration and battery cooling mode, a battery independent cooling mode, a heat pump in-automobile heating mode, a PTC (positive temperature coefficient) heat supplementing mode, a motor heat dissipation mode, a waste heat utilization mode and a defrosting mode.
Preferably, the PTC heater (10) is power adjustable according to the heat demand.
The direct heat pump automobile air conditioning system for waste heat cascade recovery provided by the embodiment of the invention has multiple working modes, can realize a linked battery heat management function, can preheat a battery and heat the inside of the automobile while defrosting, improves the in-automobile heat comfort and ensures that the battery works in a working temperature range; in addition, under the low temperature condition, the waste heat of the motor is used as a low temperature heat source to perform in-vehicle heating, so that the problems of over high exhaust temperature, obviously insufficient heating quantity and the like of the compressor when the heat pump type automobile air conditioner runs under the low temperature working condition are solved; and a plurality of highly integrated components are adopted, so that the compactness and reliability of the system are effectively improved.
Drawings
Fig. 1 is a schematic diagram of a heat pump air conditioning system architecture according to the present invention.
Fig. 2 is a schematic diagram of an operating state of the in-vehicle cooling mode according to the present invention.
Fig. 3 is a schematic diagram of the working state of the in-vehicle refrigeration and battery cooling mode according to the present invention.
Fig. 4 is a schematic diagram of an operating state of the in-vehicle cooling and dehumidifying mode according to the present invention.
Fig. 5 is a schematic diagram of a cooling operation state of an air conditioner refrigerant in a battery independent cooling mode 1 and a defrosting mode 1 according to the present invention.
Fig. 6 is a schematic diagram of the battery cooling alone mode 2, i.e. the ambient air cooling operation state according to the present invention.
Fig. 7 is a schematic diagram of the motor cooling mode according to the present invention.
Fig. 8 is a schematic diagram of the working state of the heating and battery preheating modes in the heat pump truck.
Fig. 9 is a schematic diagram of a state of operation of the battery in the warm-up mode according to the present invention.
Fig. 10 is a schematic diagram of the working state of heating and PTC concurrent heating in the heat pump truck according to the present invention.
Fig. 11 is a schematic diagram of the working state of waste heat heating+ptc heat compensation according to the present invention.
Fig. 12 is a schematic view of the operation state of the defrosting mode 2 according to the present invention.
Fig. 13 is a schematic diagram of the working state of waste heat heating and motor heat dissipation according to the invention.
In the accompanying drawings: 1. a first water pump; 2. a charging system; 3. a DC power converter; 4. a motor control system; 5. a motor; 6. a proportional five-way valve; 7. a motor radiator; 8. a motor cooling fan; 9. a first electromagnetic three-way valve; 10. a PTC heater; 11. an in-vehicle radiator; 12. a first plate heat exchanger; 13. a compressor; 14. a four-way valve; 15. an off-vehicle heat exchanger; 16. three-way valve with two-way electronic expansion valve; 17. a first in-vehicle heat exchanger; 18. an in-vehicle radiator fan; 19. a gas-liquid separator; 20. a second plate heat exchanger; 21. a second water pump; 22. a battery heat exchange module; 23. a battery radiator; 24. a battery radiator fan; 25. a third electromagnetic three-way valve; 26. an expansion pot; 27. a second electromagnetic three-way valve; 28. the second in-vehicle heat exchanger.
Detailed Description
The present invention will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present invention more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
Specific implementations of the invention are described in detail below in connection with specific embodiments.
As shown in fig. 1, a direct heat pump vehicle air conditioning system for waste heat gradient recovery according to an embodiment of the present invention includes: the waste heat temperature control circulation module, PTC heater (10), refrigerant circulation module, heat exchange module and battery temperature control module in the car, refrigerant circulation module is connected with outer heat exchanger (15) of car through cross valve (14), outer heat exchanger (15) is connected with heat exchange module and battery temperature control module in the car through the three-way valve of taking two-way electronic expansion valve, refrigerant circulation module passes through cross valve (14) and is connected with heat exchange module and battery temperature control module in the car, PTC heater (10) are installed in waste heat temperature control circulation module, waste heat temperature control circulation module is connected with battery temperature control module.
In this embodiment, there is provided a direct heat pump vehicle air conditioning system of waste heat cascade recovery, including a first water pump 1, a charging system 2, a direct current power converter 3, a motor control system 4, a motor 5, a proportional five-way valve 6, a motor radiator 7, a motor radiator fan 8, a first electromagnetic three-way valve 9, a PTC heater 10, an in-vehicle radiator 11, a first plate heat exchanger 12, a compressor 13, a four-way valve 14, an out-vehicle heat exchanger 15, a three-way valve with a two-way electronic expansion valve 16, a first in-vehicle heat exchanger 17, an in-vehicle radiator fan 18, a gas-liquid separator 19, a second plate heat exchanger 20, a second water pump 21, a battery heat exchange module 22, a battery radiator 23, a battery radiator fan 24, a third electromagnetic three-way valve 25, an expansion pot 26, a second electromagnetic three-way valve 27, and a second in-vehicle heat exchanger 28.
In this embodiment, as shown in fig. 1, the proportional five-way valve 6 includes five ports, the four-way valve 14 includes four ports, the first electromagnetic three-way valve 9, the second electromagnetic three-way valve 27 and the third electromagnetic three-way valve 25 each include three ports, five ports abcde of the proportional five-way valve 6 are respectively communicated with the motor radiator 7, the first plate heat exchanger 12, the in-vehicle radiator 11, the PTC heater 10 and the motor 5, the a port on the first electromagnetic three-way valve 9 is communicated with the first plate heat exchanger 12 and the in-vehicle radiator 11, the b port on the first electromagnetic three-way valve 9 is communicated with the motor radiator 7, the c port on the first electromagnetic three-way valve 9 is communicated with the first water pump 1 and the expansion pot 26, the a port on the second electromagnetic three-way valve 27 is communicated with the first in-vehicle heat exchanger 17, the b port and the c port on the second electromagnetic three-way valve 27 are respectively communicated with both ends of the in-vehicle heat exchanger 28, the c port on the second electromagnetic three-way valve 27 is also communicated with the b port on the four-way valve 14 and the second plate heat exchanger 20, the c port on the third electromagnetic three-way valve 27 is communicated with the third plate heat exchanger 25, the three-way valve 20 and the in-way heat exchanger 15 and the out-vehicle heat exchanger 15 are respectively communicated with the second water pump 1 and the expansion pot 26, the three-way valve 27 and the three-way heat exchanger 17.
There are two modes of operation for the three-way valve 16 with a two-way electronic expansion valve:
(1) ab communication: a bidirectional electronic expansion valve is arranged and has a bidirectional throttling function, and the bidirectional electronic expansion valve is connected with the first in-vehicle heat exchanger 17 and the out-vehicle heat exchanger 15.
(2) ac communication: a bidirectional electronic expansion valve is arranged and has a bidirectional throttling function, and the second plate heat exchanger 20 is connected with the external heat exchanger 15.
The four-way valve 14 has two modes of operation:
(1) ac communication connects the compressor 13 to the off-board heat exchanger 15, bd to the gas-liquid separator 19 to the first in-vehicle heat exchanger 17.
(2) ab is connected to the compressor 13 and the first in-vehicle heat exchanger 17, cd is connected to the gas-liquid separator 19 and the out-of-vehicle heat exchanger 15.
The proportional five-way valve 6 is provided with two inlets d and e and three outlets a, b and c, and the flow distribution proportion of each inlet and outlet is controlled by controlling the size of the inlet and outlet.
According to the invention, the valve is switched, so that the automobile air conditioner can realize various working modes; the working mode is as follows:
1. in-vehicle cooling mode: as shown in fig. 2, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port c, then enters the external heat exchanger 15 to release heat into the environment to become supercooled liquid, then enters through a port a of the three-way valve 16 with the two-way electronic expansion valve, flows out through a port b (a- > b is provided with the two-way electronic expansion valve), then enters the first internal heat exchanger 17, absorbs the heat of the air, reduces the temperature of the air, then flows in through a port a of the second electromagnetic three-way valve 27, flows out through a port b, then enters the second internal heat exchanger 28 to absorb the heat of the air again, realizes the twice temperature reduction of the air, then enters through a port b of the four-way valve 14, then flows out through a port d, then enters the gas-liquid separator 19, and finally returns to the compressor 13, thus realizing the internal refrigeration cycle. In this mode four-way valve 14 is in ac, bd communication; the three-way valve 16 with the two-way electronic expansion valve is in ab communication (ab contains the electronic expansion valve); the second electromagnetic three-way valve 27 is in the ab communication state.
In the cooling mode, when the cooling capacity is small, the second electromagnetic three-way valve 27 can be adjusted to be in an ac communication state, and the refrigerant only passes through the first in-vehicle heat exchanger 17 but not the second in-vehicle heat exchanger 28; when the refrigerating capacity is large, the second electromagnetic three-way valve 27 is adjusted to be in a state of ab communication, at this time, the first in-vehicle heat exchanger 17 and the second in-vehicle heat exchanger 28 are connected in series, and the refrigerant passes through the first in-vehicle heat exchanger 17 and the second in-vehicle heat exchanger 28 at the same time, and the switching between the large refrigerating capacity and the small refrigerating capacity is realized by adjusting the second electromagnetic three-way valve 27.
2. In-vehicle cooling+battery cooling mode: as shown in fig. 3, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port c, then enters the external heat exchanger 15 to release heat into the environment to become a supercooled liquid state, then enters through a port a of the three-way valve 16 with a two-way electronic expansion valve, a part of the refrigerant flows out through a port b (a- & gt is provided with the two-way electronic expansion valve in a passage b), then enters the first internal heat exchanger 17, the refrigerant absorbs the heat of the air, the temperature of the air is reduced, then flows in through a port a of the second electromagnetic three-way valve 27, flows out through a port c, then enters through a port b of the four-way valve 14, flows out through a port d, then enters the gas-liquid separator 19, and finally returns to the compressor 13 to realize the internal refrigeration cycle; the other part of the refrigerant flows out through a port c (a bi-directional electronic expansion valve is arranged in a channel a-c), enters the second plate heat exchanger 20 to exchange heat with battery cooling liquid, and finally returns to the compressor through the four-way valve 14 and the gas-liquid separator 19. Under the action of the second water pump 21, the battery circulating liquid flows through the battery heat exchange module 22, absorbs heat on the surface of the battery, enters the second plate heat exchanger 20, transfers the heat to the refrigerant to realize cooling, then enters through the port b of the third electromagnetic three-way valve 25, flows out through the port c, flows through the first plate heat exchanger 12, and then returns to the second water pump 21 to realize battery cooling circulation; in this mode four-way valve 14 is in ac, bd communication; the three-way valve 16 with the two-way electronic expansion valve is communicated with ab and ac (the ab and the ac contain the electronic expansion valve); the second electromagnetic three-way valve 27 is in an ac communication state; the third electromagnetic three-way valve 25 is in a bc communication state.
3. In-vehicle cooling and dehumidifying mode: as shown in fig. 4, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port c, then enters the heat exchanger 15 outside the vehicle to release heat into the environment to become a supercooled liquid state, then enters through a port a of the three-way valve 16 with a two-way electronic expansion valve, flows out through a port b (a- > b is provided with the two-way electronic expansion valve), then enters the first in-vehicle heat exchanger 17, absorbs the heat of the air, reduces the temperature of the air, then flows in through a port a of the second electromagnetic three-way valve 27, flows out through a port c, then enters through a port b of the four-way valve 14, flows out through a port d, then enters the gas-liquid separator 19, and finally returns to the compressor 13 to realize the in-vehicle refrigeration cycle. The PTC circulating heating liquid is heated by the PTC heater 10 under the action of the first water pump 1, enters through a port d of the proportional five-way valve 6, flows out through a port c, dehumidifies air through the in-vehicle radiator 11, enters through a port a of the first electromagnetic three-way valve 9, flows out through a port c, and finally returns to the water pump to realize the dehumidification process; in this mode four-way valve 14 is in ac, bd communication; the three-way valve 16 with the two-way electronic expansion valve is communicated with ab (ab contains the electronic expansion valve); the first electromagnetic three-way valve 9 is in an ac communication state.
4. 1 battery individual cooling mode 1 (air conditioning refrigerant cooling): as shown in fig. 5, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port c, enters the heat exchanger 15 outside the vehicle to release heat into the environment to become supercooled liquid, enters through a port a of the three-way valve 16 with a two-way electronic expansion valve, flows out through a port c (a- > c is provided with the two-way electronic expansion valve), exchanges heat with battery cooling liquid through the second plate heat exchanger 20, enters through a port b of the four-way valve 14, flows out through a port d, passes through the gas-liquid separator 19, and finally returns to the compressor; meanwhile, the battery cooling liquid absorbs heat through the battery heat exchange module 22 under the action of the second water pump 21, then exchanges heat with the refrigerant through the second plate heat exchanger 20, enters through a port b of the third electromagnetic three-way valve 25, flows out through a port c, and returns to the water pump through the first plate heat exchanger 12 to complete battery cooling circulation. In this mode four-way valve 14 is in ac, bd communication; the three-way valve 16 with the two-way electronic expansion valve is in ac communication (the ac contains the electronic expansion valve); the third electromagnetic three-way valve 25 is in a bc communication state.
4. 2 battery individual cooling mode 2 (ambient air cooling): as shown in fig. 6, the battery cooling liquid absorbs heat through the battery heat exchange module 22 under the action of the second water pump 21, then passes through the battery radiator 23, releases the heat under the action of the fan 24, then enters through the port a of the third electromagnetic three-way valve 25, flows out through the port c, and then returns to the water pump through the first plate heat exchanger 12, thus completing the battery cooling cycle; in this mode the third electromagnetic three-way valve 25 is in ac communication.
5. Motor cooling mode: as shown in fig. 7, the motor circulation liquid flows through the charging system 2, the direct-current power converter 3, the motor control system 4 and the motor 5 under the action of the first water pump 1, enters through a port e of the proportional five-way valve 6, flows out through a port a, then enters the motor radiator 7, the air cools the motor radiator 7 under the action of the motor cooling fan 8, and the cooled liquid returns to the first water pump 1 to realize motor cooling circulation; in this mode the proportional five-way valve 6 is in ae communication.
6. Heat pump heating+battery preheating mode: as shown in fig. 8, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port b, and is partially heat exchanged with the low-temperature cooling liquid through the second plate heat exchanger 20 to become supercooled liquid, and the other part of the refrigerant enters through a port c of the second electromagnetic three-way valve 27, flows out through the port a, passes through the first in-vehicle heat exchanger 17, releases heat under the action of the fan 18, and finally enters from a port b and a port c of the three-way valve 16 with the two-way electronic expansion valve respectively to be mixed, absorbs heat through the out-vehicle heat exchanger 15 after flowing out from the port a, then enters through a port c of the four-way valve 14, flows out through a port d, enters the gas-liquid separator 19, and finally returns to the compressor 13. The battery circulating liquid preheats the battery through the battery heat exchange module 22 under the action of the second water pump 21, absorbs heat through the second plate heat exchanger 20, enters through a port b of the third electromagnetic three-way valve 25, flows out through a port c, passes through the first plate heat exchanger 12, and finally returns to the water pump to realize battery preheating circulation; the four-way valve 14 is communicated with ab and cd; the three-way valve 16 with the two-way electronic expansion valve is communicated with ab and ac (the ab and the ac contain the electronic expansion valve); the third electromagnetic three-way valve 25 is in a bc communication state.
7. Waste heat utilization battery preheating mode: as shown in fig. 9, the motor circulating liquid flows through the charging system 2, the direct current power converter 3, the motor control system 4 and the motor 5 under the action of the first water pump 1, enters through a port e of the proportional five-way valve 6, flows out through a port b, exchanges heat with the battery circulating liquid through the first plate heat exchanger 12, enters through a port a of the first electromagnetic three-way valve 9, flows out through a port c, and finally returns to the first water pump 1; the battery circulating liquid preheats the battery through the battery heat exchange module 22 under the action of the second water pump 21, then passes through the battery radiator 23, then enters through the port a of the third electromagnetic three-way valve 25, flows out through the port c, absorbs heat through the first plate heat exchanger 12, and finally returns to the water pump to realize the battery preheating circulation. In this mode, the proportional five-way valve 6 is in be communication; the first electromagnetic three-way valve 9 is in an ac communication state; the battery three-way valve 25 is in ac communication.
8. Heat pump heating+ptc heat compensation mode: as shown in fig. 10, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port b, enters through a port c of the second electromagnetic three-way valve 27, flows out through a port a, then passes through the first in-vehicle heat exchanger 17, releases heat under the action of the fan 18, then enters through a port b of the three-way valve 16 with a two-way electronic expansion valve, flows out through a port a, enters the out-vehicle heat exchanger 15 to absorb heat, then enters through a port c of the four-way valve 14, flows out through a port d, then passes through the gas-liquid separator 19, and finally returns to the compressor to realize the heat pump heating cycle; meanwhile, PTC heating circulating liquid flows through the PTC heater 10 to be heated under the action of the first water pump 1, then enters from a port d of the proportional five-way valve 6, flows out from a port c, then heats the interior of the vehicle through the in-vehicle radiator 11 under the action of the fan 28, then enters from a port a of the first electromagnetic three-way valve 9, flows out from the port c, returns to the water pump, and realizes the heat supplementing circulation. In this mode the four-way valve 14 is in ab, cd communication; the three-way valve 16 with the two-way electronic expansion valve is communicated with ab (ab contains the electronic expansion valve); the second electromagnetic three-way valve 27 is in an ac communication state; the proportional five-way valve 6 is in a cd communication state; the first electromagnetic three-way valve 9 is in an ac communication state.
9. Waste heat heating+PTC heat supplementing mode: as shown in fig. 11, a part of circulating liquid flows through the charging system 2, the dc power converter 3, the motor control system 4 and the motor 5 under the action of the first water pump 1, enters through a port e of the proportional five-way valve 6, and enters through a port d of the proportional five-way valve 10, and after being mixed, flows out through a port c, flows out through the in-vehicle radiator 11, releases heat under the action of the fan 28, then enters through a port a of the first electromagnetic three-way valve 9, flows out through a port c, returns to the water pump, and achieves waste heat and complementary heating circulation. The proportional five-way valve 6 is in a cde communication state in the mode; the first electromagnetic three-way valve 9 is in an ac communication state.
10. Defrost mode 1 (battery thermal defrost): as shown in fig. 5, the high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port c, enters the external heat exchanger 15 to release heat to finish defrosting, enters through a port a of the three-way valve 16 with a bidirectional electronic expansion valve, flows out through a port c (a- & gtc channel is provided with a bidirectional electronic expansion valve), exchanges heat with battery cooling liquid through the second plate heat exchanger 20, enters through a port b of the four-way valve 14, flows out through a port d, passes through the gas-liquid separator 19, and finally returns to the compressor; meanwhile, the battery cooling liquid absorbs heat through the battery heat exchange module 22 under the action of the second water pump 21, then exchanges heat with the refrigerant through the second plate heat exchanger 20, enters through a port b of the third electromagnetic three-way valve 25, flows out through a port c, and returns to the water pump through the first plate heat exchanger 12 to complete battery cooling circulation; in this mode four-way valve 14 is in ac, bd communication; the three-way valve 16 with the two-way electronic expansion valve is in ac communication (the ac contains the electronic expansion valve); the third electromagnetic three-way valve 25 is in a bc communication state.
10. Defrost mode 2 (PTC preheat battery while defrost): as shown in fig. 12, the PTC heating circulation liquid flows through the PTC heater 10 to be heated by the first water pump 1, then enters from the port d of the proportional five-way valve 6, exits from the port b, exchanges heat with the battery circulation liquid in the first plate heat exchanger 12, then enters through the port a of the first electromagnetic three-way valve 9, exits from the port c, and finally returns to the water pump. Meanwhile, battery circulating liquid preheats the battery through the battery heat exchange module 22 under the action of the second water pump 21, heats the refrigerant through the second plate heat exchanger 20, enters through a port b of the third electromagnetic three-way valve 25, flows out through a port c, absorbs heat through the first plate heat exchanger 12, and finally returns to the water pump, so that the battery preheating circulation is realized, and part of heat is transferred to the refrigerant. The high-temperature and high-pressure refrigerant compressed by the compressor 13 enters through a port a of the four-way valve 14, flows out through a port c, enters the off-vehicle heat exchanger 15 to release heat to finish defrosting, enters through a port a of the three-way valve 16 with a two-way electronic expansion valve, flows out through the port c (a- & gt is provided with the two-way electronic expansion valve in a channel C), exchanges heat with battery circulating liquid through the second plate heat exchanger 20, enters through a port b of the four-way valve 14, flows out through a port d, passes through the gas-liquid separator 19, and finally returns to the compressor. In this mode four-way valve 14 is in ac, bd communication; the three-way valve 16 with the two-way electronic expansion valve is in ac communication (the ac contains the electronic expansion valve); the third electromagnetic three-way valve 25 is in a bc communication state; the proportional five-way valve 6 is in bd communication; the first electromagnetic three-way valve 9 is in an ac communication state.
11. Waste heat heating+motor heat dissipation mode: as shown in fig. 13, the circulating liquid flows through the charging system 2, the dc power converter 3, the motor control system 4, and the motor 5 under the action of the first water pump 1, enters through a port e of the proportional five-way valve 6, and flows out through a port b, passes through the radiator 11, and heats the interior of the vehicle under the action of the fan 28; the other part of circulating liquid flows out through a port a of the proportional five-way valve 6, passes through the external radiator 7, radiates heat under the action of the fan 8, and then enters through a port a and a port b of the first electromagnetic three-way valve 9 respectively, flows out from a port c and returns to the water pump; in this mode the proportional five-way valve 6 is in the ace communication state.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.

Claims (7)

1. A direct heat pump automotive air conditioning system for waste heat gradient recovery, the system comprising: the waste heat temperature control circulation module, PTC heater (10), refrigerant circulation module, heat exchange module and battery temperature control module in the car, refrigerant circulation module is connected with outer heat exchanger (15) of car through cross valve (14), outer heat exchanger (15) is connected with heat exchange module and battery temperature control module in the car through the three-way valve of taking two-way electronic expansion valve, refrigerant circulation module passes through cross valve (14) and is connected with heat exchange module and battery temperature control module in the car, PTC heater (10) are installed in waste heat temperature control circulation module, waste heat temperature control circulation module is connected with battery temperature control module.
2. The direct heat pump vehicle air conditioning system according to claim 1, wherein the waste heat temperature control circulation module comprises a first water pump (1), a proportional five-way valve (6), an in-vehicle radiator (11), a motor radiator (7) and a motor radiator fan (8), the first water pump (1) passes through a charging system (2), a direct current power supply converter (3), a motor control system (4) and a motor (5) through a pipeline and is connected with the proportional five-way valve (6), one end of the motor radiator (7) is connected with the proportional five-way valve (6), the other end of the motor radiator is connected with a first electromagnetic three-way valve (9), the motor radiator fan (8) is arranged on one side of the motor radiator (7), one end of a PTC heater (10) is connected with the proportional five-way valve (6), the other end of the first water pump (1) is connected with a battery temperature control module through the first electromagnetic three-way valve (9), one end of the in-vehicle radiator (11) is connected with the proportional five-way valve (6), the other end of the motor radiator fan is connected with the first electromagnetic three-way valve (9) and the battery temperature control three-way valve (26) is connected with the first electromagnetic three-way valve (1), and the expansion valve (26) is connected with the battery temperature control three-way valve (1).
3. The direct heat pump vehicle air conditioning system according to claim 1, wherein the refrigerant cycle module includes a compressor (13) and a gas-liquid separator (19), one end of the compressor (13) is connected to the gas-liquid separator (19), and the other end is connected to the four-way valve (14), and the gas-liquid separator (19) is also connected to the four-way valve (14).
4. The direct heat pump vehicle air conditioning system according to claim 2, wherein the in-vehicle heat exchange module comprises a first in-vehicle heat exchanger (17), an in-vehicle radiator fan (18) and a second in-vehicle heat exchanger (28), one end of the first in-vehicle heat exchanger (17) is connected with the proportional five-way valve (6), the other end is connected with a second electromagnetic three-way valve (27), two ports of the second electromagnetic three-way valve (27) are connected with two ends of the second in-vehicle heat exchanger (28), and the second electromagnetic three-way valve (27) is also communicated with the four-way valve (14) and the battery temperature control module.
5. The direct heat pump automobile air conditioning system with the step recovery of waste heat according to claim 2, wherein the battery temperature control module comprises a first plate heat exchanger (12), a second plate heat exchanger (20), a second water pump (21), a battery heat exchange module (22), a third electromagnetic three-way valve (25) and a battery radiator (23), three ports of the third electromagnetic three-way valve (25) are respectively connected with the first plate heat exchanger (12), the second plate heat exchanger (20) and the battery radiator (23), one end of the battery radiator (23) far away from the third electromagnetic three-way valve (25) is simultaneously connected with the second plate heat exchanger (20) and the battery heat exchange module (22), two ends of the second water pump (21) are respectively connected with the first plate heat exchanger (12) and the battery heat exchange module (22), and the first plate heat exchanger (12) is connected with the proportional five-way valve (6) and the first electromagnetic three-way valve (9).
6. The direct heat pump vehicle air conditioning system of claim 1, wherein the direct heat pump vehicle air conditioning system of the waste heat step recovery comprises an in-vehicle cooling mode, an in-vehicle cooling while battery cooling mode, a battery independent cooling mode, a heat pump in-vehicle heating mode, a PTC supplemental heating mode, a motor heat dissipation mode, a waste heat utilization mode, and a defrost mode.
7. Direct heat pump vehicle air conditioning system with cascade recovery of waste heat according to claim 1, characterized in that the PTC heater (10) is power adjustable according to the heat demand.
CN202310287802.4A 2023-03-23 2023-03-23 Direct heat pump automobile air conditioning system for waste heat gradient recovery Pending CN116215176A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310287802.4A CN116215176A (en) 2023-03-23 2023-03-23 Direct heat pump automobile air conditioning system for waste heat gradient recovery

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310287802.4A CN116215176A (en) 2023-03-23 2023-03-23 Direct heat pump automobile air conditioning system for waste heat gradient recovery

Publications (1)

Publication Number Publication Date
CN116215176A true CN116215176A (en) 2023-06-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310287802.4A Pending CN116215176A (en) 2023-03-23 2023-03-23 Direct heat pump automobile air conditioning system for waste heat gradient recovery

Country Status (1)

Country Link
CN (1) CN116215176A (en)

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