CN112208295B - Indirect low-temperature heat pump system - Google Patents
Indirect low-temperature heat pump system Download PDFInfo
- Publication number
- CN112208295B CN112208295B CN202010999997.1A CN202010999997A CN112208295B CN 112208295 B CN112208295 B CN 112208295B CN 202010999997 A CN202010999997 A CN 202010999997A CN 112208295 B CN112208295 B CN 112208295B
- Authority
- CN
- China
- Prior art keywords
- cooling liquid
- temperature
- heat
- low
- refrigerant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
- B60H1/32284—Cooling devices using compression characterised by refrigerant circuit configurations comprising two or more secondary circuits, e.g. at evaporator and condenser side
-
- 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
- B60H1/00007—Combined heating, ventilating, or cooling devices
-
- 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
- B60H1/00321—Heat exchangers for air-conditioning devices
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
An indirect cryogenic heat pump system comprising: the refrigerant circuit comprises an electric compressor, a high-pressure refrigerant-cooling liquid heat exchanger, a drying liquid storage tank and a low-pressure refrigerant-cooling liquid heat exchanger which are sequentially connected to form a refrigerant circuit, wherein: the refrigerant loop and the cooling liquid loop are completely independent, the high-pressure refrigerant-cooling liquid heat exchanger and the indoor heater form a high-temperature cooling liquid loop, and the low-pressure refrigerant-cooling liquid heat exchanger, the first expansion kettle, the driving motor, the radiating water tank and the heating water PTC for increasing the temperature of the low-temperature heat source form a low-temperature cooling liquid loop. The refrigerant circuit design is simplified through compression, the refrigerant leakage risk is reduced, the refrigerant charging amount is reduced, and the safety of the R290 heat pump air conditioner is improved; the automobile air conditioner has the functions of refrigerating, heating, demisting and defrosting of the passenger compartment of the new energy automobile, and can still normally operate the heat pump to heat under the low-temperature environment through the air supplementing compressor and the heating water PTC.
Description
Technical Field
The invention relates to a technology in the field of heat pump air conditioners, in particular to an indirect low-temperature heat pump system adopting propane (R290).
Background
The existing automobile air conditioning system is refrigerated by an air conditioning system, and the heating is carried out by engine coolant to dissipate heat, but the problem is solved by adopting a vehicle-mounted heat pump system or a high-voltage electric heating PTC on a new energy electric vehicle, however, the efficiency of the electric heating PTC is always smaller than 1, the energy of a battery is consumed greatly, and the endurance mileage of the whole vehicle is greatly reduced.
R290 becomes a hot door substitute refrigerant of an automobile air conditioner by virtue of the advantages of low GWP value, high latent heat of vaporization, higher evaporation pressure, low price and the like, but the R290 refrigerant has many limitations in practical popularization and application due to the flammability of the R290 refrigerant and the limit of the legislation on the charging amount of the flammable refrigerant. Especially, when aiming at the characteristics of multiple heat exchangers of a heat pump air conditioner of a new energy automobile, such as multiple functions of refrigeration, heating, defogging and defrosting and complex pipelines, the leakage risk of the R290 is increased, the charging amount is increased, and the application limitation of the R290 is aggravated.
In addition, because the heat pump air conditioner of the prior new energy automobile only operates at the ambient temperature of more than minus 10 ℃ due to the limitations of low evaporation pressure and large compression ratio of a compressor, the influence of the heating of a carriage at the ambient temperature of less than minus 10 ℃ on the endurance mileage of the whole automobile is greatly aggravated.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides an indirect low-temperature heat pump system based on R290, which simplifies the design of a refrigerant loop through compression, reduces the leakage risk of the refrigerant, reduces the refrigerant charge amount and improves the safety of an R290 heat pump air conditioner; the automobile air conditioner has the functions of refrigerating, heating, defogging and defrosting of the passenger compartment of the new energy automobile, and can still normally operate the heat pump to heat in a low-temperature environment through the air supplementing compressor and the heating water PTC.
The invention is realized by the following technical scheme:
the invention comprises the following steps: the refrigerant circuit comprises an electric compressor, a high-pressure refrigerant-cooling liquid heat exchanger, a drying liquid storage tank and a low-pressure refrigerant-cooling liquid heat exchanger which are sequentially connected to form a refrigerant circuit, wherein: the refrigerant loop and the cooling liquid loop are completely independent, the high-pressure refrigerant-cooling liquid heat exchanger and the indoor heater form a high-temperature cooling liquid loop, and the low-pressure refrigerant-cooling liquid heat exchanger, the first expansion kettle, the driving motor, the radiating water tank and the heating water PTC for increasing the temperature of the low-temperature heat source form a low-temperature cooling liquid loop.
The high-temperature cooling liquid loop comprises: second water pump, indoor heater, have indoor cooler and the battery of air-blower, wherein: the second expansion kettle is connected with the indoor cooler and the battery through a third three-way water valve, the high-pressure refrigerant-cooling liquid heat exchanger is connected with the high-temperature cooling liquid loop and the indoor heater through a fourth three-way water valve and a fifth three-way water valve, the battery is connected with the indoor cooler and the high-temperature cooling liquid loop through a sixth three-way water valve, and the second water pump is arranged between the high-pressure refrigerant-cooling liquid heat exchanger and the high-temperature cooling liquid loop.
The low-temperature coolant circuit includes: first expansion kettle, driving motor, the heat dissipation water tank that has cooling fan, heating water PTC and first water pump, wherein: the driving motor is connected with the heat dissipation water tank through a first three-way water valve, the heating water PTC and the low-pressure refrigerant-cooling liquid heat exchanger are connected through a first water pump, and the low-pressure refrigerant-cooling liquid heat exchanger is connected with the first expansion kettle and the low-temperature cooling liquid loop through a second three-way water valve.
The electric compressor is an electric compressor with air supplement, and an air supplement VPI plate heat exchanger connected with an air supplement end of the electric compressor with air supplement is correspondingly arranged between the drying liquid storage tank and the low-pressure refrigerant-cooling liquid heat exchanger.
Technical effects
Compared with the prior art, the invention has the technical effects that:
1. by adopting the R290 refrigerant, the advantages of low GWP value, high latent heat of vaporization, higher evaporation pressure, low price and the like can be utilized to accelerate the substitution of the refrigerant of the heat pump system;
2. through the compact design of four major components of a condenser, an evaporator, a throttle valve and a compressor on the refrigerant side and the free combination and switching of a high-low temperature loop of a cooling liquid loop, the refrigeration, heating, demisting and defrosting functions of the heat pump air conditioner of the new energy automobile are realized, and meanwhile, the refrigerant pipeline is simplified to the greatest extent, the leakage risk of the refrigerant is reduced, the refrigerant charge is reduced, and the safety of the R290 heat pump air conditioner is improved;
3. by applying the air supply compressor, the heating capacity of the heat pump air conditioner is improved by utilizing an air supply enthalpy increasing mode, and meanwhile, the exhaust temperature under the same compression ratio is reduced, so that the heat pump air conditioner can operate under the working conditions of lower ambient temperature and larger compression ratio;
4. the adoption of the PTC heating water can improve the temperature of a low-temperature heat source of the heat pump air conditioner, and simultaneously, the characteristics of the evaporation latent heat and the higher evaporation pressure of the R290 body height can ensure that the heat pump air conditioner can normally operate at the ambient temperature of-20 ℃ or even below the ambient temperature of-30 ℃, thereby relieving the influence of the heating of the lower compartment in the low-environment temperature on the whole cruising range of the vehicle.
Drawings
Fig. 1 is a schematic diagram illustrating a refrigerant flow and a coolant flow path in a first cooling mode of operation in embodiment 1;
in the figure: the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 2 is a schematic diagram illustrating the flow paths of the refrigerant and the cooling liquid in the second cooling mode of operation in embodiment 1;
in the figure: the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 3 is a schematic path diagram of the refrigerant flow and the coolant flow in the first heating mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 4 is a schematic path diagram of the refrigerant flow and the coolant flow in the second heating mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 5 is a schematic path diagram of the refrigerant flow and the coolant flow in the third heating mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 6 is a schematic path diagram of the refrigerant flow and the coolant flow in the fourth heating mode and the fifth heating mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 7 is a schematic path diagram of the refrigerant flow and the coolant flow in the sixth heating mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 8 is a schematic path diagram of the refrigerant flow and the coolant flow in the seventh heating mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 9 is a schematic diagram illustrating the flow of the refrigerant and the flow of the cooling fluid in the first cooling and heating defogging mode according to embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
fig. 10 is a schematic diagram illustrating the flow paths of the refrigerant and the cooling fluid in the second cooling and heating demisting mode of the embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
FIG. 11 is a schematic diagram illustrating the flow paths of the cooling medium and the cooling liquid when the cooling water tank is operated in the defrosting mode in accordance with embodiment 1;
the dotted line part represents a non-flow state, the solid line represents a refrigerant flow path, the thin dashed line represents a low-temperature coolant flow path, and the thick dashed line represents a high-temperature coolant flow path;
FIG. 12 is a schematic structural view of embodiment 2;
in the figure: the system comprises a 1-stage air-supplementing electric compressor, a 2-stage high-pressure refrigerant-cooling liquid heat exchanger, a 3-stage drying liquid storage tank, a 4-stage air-supplementing VPI plate heat exchanger, a 5-stage air-supplementing VPI electronic expansion valve, a 6-stage main-path electronic expansion valve, a 7-stage low-pressure refrigerant-cooling liquid heat exchanger, an 8-stage heating water PTC, a 9-stage first water pump, a 10-stage expansion water kettle, a 11-stage drive motor, a 12-stage three-way water valve, a 13-stage heat dissipation water tank, a 14-stage cooling fan, a 15-stage second three-way water valve, a 16-stage second expansion water valve, a 17-stage third three-way water valve, a 18-stage second water pump, a 19-stage fourth three-way water valve, a 20-stage three-way water valve, a 21-stage indoor heater, a 22-stage indoor cooler, a 23-stage blower, a 24-stage six-way water valve and a 25-stage battery.
Detailed Description
Example 1
As shown in fig. 1 to fig. 11, the present embodiment relates to an indirect low-temperature heat pump system using R290, which includes: the air supply electric compressor 1, the high-pressure refrigerant-cooling liquid heat exchanger 2, the drying liquid storage tank 3, the air supply VPI plate heat exchanger 4 and the low-pressure refrigerant-cooling liquid heat exchanger 7 are sequentially connected to form a refrigerant loop, wherein: the outlet end of the air supply side of the air supply VPI plate type heat exchanger 4 is connected with an air supply port of the electric compressor 1 with air supply, the high-pressure refrigerant-cooling liquid heat exchanger 2 and the indoor heater 21 form a high-temperature cooling liquid loop, and the low-pressure refrigerant-cooling liquid heat exchanger 7, the first expansion kettle 10, the driving motor 11, the heat dissipation water tank 13 and the heating water PTC8 form a low-temperature cooling liquid loop.
The high-temperature cooling liquid loop comprises: a second expansion water kettle 16, a third three-way water valve 17, a second water pump 18, a fourth three-way water valve 19, a fifth three-way water valve 20, an indoor heater 21, an indoor cooler 22 with a blower 23, a sixth three-way water valve 24 and a battery 25, wherein: the second expansion water bottle 16 is connected with the indoor cooler 22 and the battery 25 through a third three-way water valve 17, the high-pressure refrigerant-cooling liquid heat exchanger 2 is connected with the high-temperature cooling liquid loop and the indoor heater 21 through a fourth three-way water valve 19 and a fifth three-way water valve 20, the battery 25 is connected with the indoor cooler 22 and the high-temperature cooling liquid loop through a sixth three-way water valve 24, and the second water pump 18 is arranged between the high-pressure refrigerant-cooling liquid heat exchanger 2 and the high-temperature cooling liquid loop.
The low-temperature coolant circuit includes: second three-way water valve 15, first expansion kettle 10, driving motor 11, first three-way water valve 12, have cooling fan 14's heat dissipation water tank 13, add hot water PTC8, first water pump 9, wherein: the driving motor 11 is connected with the heat radiation water tank 13 through a first three-way water valve 12, the heating water PTC8 is connected with the low-pressure refrigerant-cooling liquid heat exchanger 7 through a first water pump 9, and the low-pressure refrigerant-cooling liquid heat exchanger 7 is connected with the first expansion kettle 10 and the low-temperature cooling liquid loop through a second three-way water valve 15.
In the embodiment, the refrigerant loop only comprises the necessary compressor, two plate heat exchangers, a VPI module, an expansion valve and a liquid storage tank, so that the extremely compact design and complete isolation from the outside of a passenger compartment are realized mainly by completely independent refrigerant loop and cooling liquid loop, and the pipeline size of the refrigerant loop is greatly reduced.
The cooling in the passenger compartment is performed by the indoor cooler 22, and the heating is performed by the indoor heater 21, both using the coolant as the coolant/heat-transfer agent, and exchanging heat with the refrigerant circuit by a combination of a plurality of coolant three-way valves. Therefore, only when the cooling liquid enters the passenger compartment, the refrigerant circuit is completely isolated from the outside of the passenger compartment with new energy, on one hand, the compact design of the refrigerant circuit is facilitated, on the other hand, the refrigerant can be isolated from the outside of the firewall of the passenger compartment, and the explosion risk of R290 is reduced.
The heating water PTC is arranged on the low-temperature side compensation heat source, and is beneficial to improving the temperature of the low-temperature heat source in the low-temperature environment, so that the energy efficiency of the heat pump system is further improved, and the heat pump system is more effective than the heat supply of the high-temperature side compensation, so that the two technologies of air supply and enthalpy increase and R290 are combined in the embodiment, and the heating water PTC is used for supplementing the low-temperature heat source to realize the expansion of the low-temperature range of the operation of the heat pump air conditioner.
The embodiment relates to a heat exchange method of the indirect low-temperature heat pump system adopting the R290, which comprises the following steps: two kinds of refrigeration mode, seven heating modes, two kinds of refrigeration and heating demisting mode and heat dissipation water tank defrosting mode.
The first refrigeration mode specifically includes: the high-temperature and high-pressure gaseous refrigerant discharged from the electric compressor with air supplement 1 flows into the high-pressure refrigerant-cooling liquid heat exchanger 2 for condensation and heat exchange, so that the effect of heating the cooling liquid on the other side of the heat exchanger is achieved. The condensed refrigerant flows out of the heat exchanger 2 and enters the drying liquid storage tank 3 to realize the gas-liquid separation effect, and the refrigerant flowing out of the liquid storage tank 3 is ensured to be liquid. The refrigerant is divided into two parts at the outlet of the liquid storage tank 3: one path of refrigerant reaches an inlet of the air-supplementing VPI electronic expansion valve 5 along a branch, flows into one side of the air-supplementing VPI plate type heat exchanger 4 to absorb heat after isenthalpic throttling, and flows out of the heat exchanger 4 to reach an air-supplementing port of the compressor 1 to enter the compressor after the refrigerant which is changed into a medium-pressure overheat state flows into the heat exchanger 4; the other path of refrigerant directly reaches the other side of the air-supplementing VPI plate type heat exchanger 4 along the main path to release heat, the refrigerant which is changed into a high-pressure supercooled state flows out of the heat exchanger 4 to reach the inlet of the main path electronic expansion valve 6, and the refrigerant flows into the low-pressure refrigerant-cooling liquid heat exchanger 7 after isenthalpic throttling to evaporate and absorb heat, so that the effect of cooling the cooling liquid on the other side of the heat exchanger is achieved. Finally, the low pressure superheated refrigerant flowing from the heat exchanger 7 returns to the compressor suction to begin the next cycle.
In this mode, the cooling liquid loop can be divided into a high temperature portion and a low temperature portion according to the temperature of the cooling liquid, wherein the high temperature cooling liquid loop is used for taking away heat released by condensation of the refrigerant in the heat exchanger 2 and heat released by the driving motor 11; the low-temperature cooling liquid circuit is used for conveying cooling liquid cooled by the heat exchanger 7 to the indoor cooler 22, so that the effect of cooling air in the vehicle compartment is achieved.
In the high-temperature cooling liquid loop, the cooling liquid cooled by the heat-radiating water tank 13 reaches the inlet of the second water pump 18, the cooling liquid is pumped into the heat exchanger 2 by the water pump to absorb the condensation heat emitted by the refrigerant on the other side, and the heated cooling liquid returns to the inlet of the first expansion water kettle 10 through the fourth three-way water valve 19. The cooling liquid flowing out of the first expansion water tank 10 reaches the inlet of the cooling module of the driving motor 11, the cooling liquid absorbs the heat dissipated by the driving motor to further raise the temperature, and the high-temperature cooling liquid flows out of the driving motor 11, returns to the heat dissipation water tank 13 through the first three-way water valve 12 to be cooled, and then starts the next cycle.
In the low-temperature cooling liquid loop, cooling liquid sent into the low-pressure refrigerant-cooling liquid heat exchanger 7 by the first water pump 9 is cooled by a refrigerant on the other side, then flows through the second three-way water valve 15 to reach an inlet of the third three-way water valve 17, and all cooling liquid flowing out of the third three-way water valve 17 flows into the indoor cooler 22, so that air flowing through the surface of the fins of the indoor cooler 22 is cooled, and the effect of cooling a carriage is achieved. The heat-absorbed cooling liquid flows out of the indoor cooler and returns to the inlet of the first water pump 9 through the heating water PTC8 to start the next circulation, and the heating water PTC does not work in the mode.
In the second refrigeration mode, the refrigerant circuit and the high-temperature cooling liquid circuit are consistent with the first refrigeration mode, only a part of cooling liquid flowing out of the third three-way water valve 17 in the low-temperature cooling liquid circuit needs to flow into the cooling module of the battery 25 according to the thermal load of the battery, and the rest of cooling liquid flows into the indoor cooler 22, so that the effect of refrigerating the battery and the compartment at the same time is achieved.
In the first heating mode, the refrigerant circuit is kept consistent with the cooling mode, and only the high-temperature circuit and the low-temperature circuit of the cooling liquid need to be reorganized. In the low-temperature cooling liquid loop, the heat of the cooling liquid sent into the low-pressure refrigerant-cooling liquid heat exchanger 7 by the first water pump 9 is absorbed by the refrigerant on the other side, and then the temperature is reduced, and the low-temperature cooling liquid passes through the second three-way water valve 15 and reaches the inlet of the first expansion kettle 10. The coolant flowing out of the first expansion pot 10 reaches the inlet of the cooling module of the driving motor 11, which is suitable for the idling mode of the vehicle, in which the heat of the motor is small and the temperature rise of the coolant is small. The cooling liquid flowing out of the driving motor 11 returns to the inlet of the radiating water tank 13 through the first three-way water valve 12, the temperature of the cooling liquid absorbing the air blown across the surface of the fins of the water tank is increased, the heated cooling liquid flows back to the inlet of the first water pump 9 through the heating water PTC8, the next circulation is started, and the heating water PTC does not work in the mode.
In the high-temperature cooling liquid loop, the cooling liquid sent into the high-pressure refrigerant-cooling liquid heat exchanger 2 through the second water pump 18 absorbs the condensation heat of the refrigerant on the other side of the heat exchanger 2, and the heated cooling liquid reaches the inlet of the fifth three-way water valve 20 through the fourth three-way water valve 19. The coolant flowing out of the fifth three-way water valve 20 flows into the indoor heater 21, so that the temperature of the air flowing through the surface of the fins of the indoor heater 21 is raised, the effect of heating the carriage is achieved, and the cooled coolant flows out of the indoor heater and then returns to the inlet of the second water pump 18 to start the next cycle.
In the second heating mode, the refrigerant circuit and the low-temperature coolant circuit are consistent with the first heating mode, only the coolant flowing out of the fifth three-way water valve 20 in the high-temperature coolant circuit needs to be divided into a part of coolant to flow into the cooling module of the battery 25 according to the heating requirement of the battery, and the rest of the coolant flows into the indoor heater 21, so that the effect of heating the battery and the compartment at the same time is achieved.
In the third heating mode, the refrigerant loop and the high-temperature cooling liquid loop are consistent with the first heating mode, but the low-temperature cooling liquid flowing out of the second three-way water valve 15 needs to be divided into one path and flows into the cooling module of the battery 25 through the second expansion water tank 16 and the third three-way water valve 17, and the waste heat of the battery is absorbed and utilized as a second low-temperature heat source. The cooling liquid flowing out of the battery 25 passes through the sixth three-way water valve 24 and then is mixed with the cooling liquid flowing out of the radiating water tank 13, and then returns to the inlet of the first water pump 9 through the heating water PTC8 to start the next circulation, and in the mode, the heating water PTC does not work.
In the fourth heating mode, the refrigerant loop and the high-temperature cooling liquid loop are consistent with the second heating mode, but the low-temperature heat source of the heat pump in the low-temperature cooling liquid loop is different, and the mode is suitable for the driving working condition and absorbs the heat dissipation capacity of the motor to complete the heat pump circulation. The low-temperature coolant flows through the second three-way water valve 15 to reach the inlet of the first expansion kettle 10, the coolant flowing out of the first expansion kettle 10 reaches the inlet of the cooling module of the driving motor 11, the motor is in high-speed operation at the moment, the heat dissipation capacity is large, and the temperature of the coolant is increased greatly after the coolant flows through the driving motor. The cooling liquid flowing out of the driving motor 11 bypasses the heat dissipation water tank 13 through the first three-way water valve 12, does not exchange heat with the external environment, flows through the heating water PTC8 and returns to the inlet of the first water pump 9 to start the next cycle, and the heating water PTC does not work in the mode.
In the fifth heating mode, the system schematic diagram is consistent with the fourth heating mode, but at the moment, the heating water PTC8 starts to work to provide a low-temperature heat source, and the low-temperature cooling liquid loop does not exchange heat with the external environment, so that the heat pump can still normally operate at a lower environmental temperature.
In the sixth heating mode, the refrigerant circuit is consistent with the fourth heating mode, but the high-temperature circuit and the low-temperature circuit of the cooling liquid need to be reorganized. In the low-temperature cooling liquid loop, the low-temperature cooling liquid flowing out of the second three-way water valve 15 needs to be divided into one path, flows into the cooling module of the battery 25 through the second expansion kettle 16 and the third three-way water valve 17, and absorbs and utilizes the waste heat of the battery as a second low-temperature heat source. The cooling liquid flowing out of the battery 25 passes through the sixth three-way water valve 24 and then is mixed with the cooling liquid flowing out of the radiating water tank 13, and then returns to the inlet of the first water pump 9 through the heating water PTC8 to start the next circulation, and in the mode, the heating water PTC does not work. Accordingly, in the high-temperature coolant circuit, all of the coolant flowing out of the fifth three-way water valve 20 flows into the indoor heater 21 to heat the vehicle compartment, and the flow of the high-temperature coolant into the water circuit of the battery is blocked.
And the seventh heating mode is used for directly heating the carriage by utilizing the heat of the motor when the heating demand of the carriage is not large, and the refrigerant loop does not work at the moment. The cooling liquid flows through the heat exchanger 2 from the outlet of the second water pump 18 and then reaches the inlet of the fourth three-way water valve 19, and the outlet of the fourth three-way water valve 19 is divided into two parts: one path of cooling liquid completely flows into the indoor heater 21 through the fifth three-way water valve 20 to heat air blown on the surface of the indoor heater fin, so that the effect of heating the carriage is achieved; and the other path of cooling liquid absorbs the heat released by the driving motor 11 after flowing through the first expansion water bottle 10, bypasses the heat dissipation water tank 13 by using the first three-way water valve 12, returns to the inlet of the second water pump 18 and is merged with the low-temperature cooling liquid at the outlet of the indoor heater 21, and the temperature of the mixed cooling liquid is increased to start the next cycle.
The first refrigerating and heating demisting mode is used for the working condition that the compartment has refrigerating and dehumidifying requirements and heating and warming requirements at the same time, the refrigerant loop and the low-temperature cooling liquid loop are kept consistent with the first refrigerating mode in the first refrigerating mode, and compared with a high-temperature cooling liquid loop in the first refrigerating mode, the mode divides the outlet cooling liquid of the fourth three-way water valve 19 into two parts, introduces one path of high-temperature cooling liquid to flow into the indoor heater 21 to heat the compartment, and meets the requirement of heating and warming the compartment.
The second refrigerating and heating demisting mode is used for the working condition that the carriage has larger heating and warming requirements, and the refrigerant loop and the low-temperature cooling liquid loop are consistent with the first refrigerating and heating demisting mode in the mode. In the high-temperature cooling liquid loop, the low-temperature cooling liquid which bypasses the radiator tank 13 by using the first three-way water valve 12 returns to the inlet of the second water pump 18 and is merged with the low-temperature cooling liquid at the outlet of the indoor heater 21. At this time, the high-temperature heat is not released to the environment through the heat dissipation water tank 13, and the temperature of the coolant entering the second water pump 18 after mixing can be further increased, so that a greater heating and warming requirement of the carriage is met.
The defrosting mode of the heat radiation water tank is used for defrosting a heat radiation water tank by utilizing the heating capacity of the heat pump, and a refrigerant loop is consistent with a refrigeration mode in the defrosting mode. In the high-temperature cooling liquid loop, the cooling liquid sent into the high-pressure refrigerant-cooling liquid heat exchanger 2 through the second water pump 18 absorbs the condensation heat of the refrigerant on the other side of the heat exchanger 2, and the heated cooling liquid reaches the inlet of the first expansion water bottle 10 through the fourth three-way water valve 19. The cooling liquid flowing out of the first expansion water bottle 10 reaches the inlet of the cooling module of the driving motor 11, the cooling liquid absorbs the heat dissipated by the driving motor to further raise the temperature, the high-temperature cooling liquid flows out of the driving motor 11, returns to the heat dissipation water tank 13 through the first three-way water valve 12 to dissipate heat and defrost, and the cooling liquid flowing out of the heat dissipation water tank returns to the inlet of the second water pump 18 to start the next circulation.
In the low-temperature cooling liquid loop, the heat of the cooling liquid sent into the low-pressure refrigerant-cooling liquid heat exchanger 7 by the first water pump 9 is absorbed by the refrigerant on the other side, then the temperature is reduced, the low-temperature cooling liquid flows to the second expansion water pot 16 through the second three-way water valve 15, flows into the cooling module of the battery 25 through the second expansion water pot 16 and the third three-way water valve 17, and absorbs and utilizes the waste heat of the battery as a low-temperature heat source. The cooling liquid flowing out of the battery 25 returns to the inlet of the first water pump 9 through the sixth three-way water valve 24 and the heating water PTC8 to start the next cycle.
Example 2
As shown in fig. 12, the present embodiment relates to a heat pump system, and the heat pump system can be safely and stably operated at a lower ambient temperature by replacing the electric compressor with air make-up with a common electric compressor, and also by designing a complete indirect heat pump using R290 refrigerant, and by matching with the use of PTC for heating water at a low temperature side and the characteristic of a higher evaporation pressure in the heating operation of R290.
The invention obviously reduces the refrigerant charge of the heat pump system by the extremely compact design of the refrigerant circuit, so that the refrigerant charge can be reduced to one fraction of the normal charge, thereby reducing the annual leakage of R290 and reducing the safety risk of R290. The characteristic that the refrigerant circuit is completely isolated from the passenger compartment of the new energy vehicle can ensure that the R290 with combustible and explosive characteristics does not enter the passenger compartment to be in close contact with passengers, and the refrigerant can be isolated from the firewall of the passenger compartment, so that the explosion risk of the R290 is reduced. The expansion of the low-temperature range of the heat pump air conditioner can ensure that the heat pump air conditioner can normally run at the ambient temperature of 20 ℃ below zero or even below 30 ℃ below zero, and the influence of the heating of the carriage at low ambient temperature on the whole cruising mileage of the vehicle is relieved.
The foregoing embodiments may be modified in many different ways by those skilled in the art without departing from the spirit and scope of the invention, which is defined by the appended claims and all changes that come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.
Claims (7)
1. An indirect cryogenic heat pump system comprising: the electric compressor, the high-pressure refrigerant-cooling liquid heat exchanger, the drying liquid storage tank and the low-pressure refrigerant-cooling liquid heat exchanger which are sequentially connected to form a refrigerant loop, wherein: the refrigerant loop and the cooling liquid loop are completely independent, the high-pressure refrigerant-cooling liquid heat exchanger and the indoor heater form a high-temperature cooling liquid loop, and the low-pressure refrigerant-cooling liquid heat exchanger, the first expansion kettle, the driving motor, the heat dissipation water tank and the heating water PTC for increasing the temperature of the low-temperature heat source form a low-temperature cooling liquid loop;
the high-temperature cooling liquid loop comprises: second water pump, indoor heater, indoor cooler and the battery that has the air-blower, wherein: the second expansion kettle is connected with an indoor cooler for refrigerating in a passenger cabin and a battery through a third three-way water valve, the high-pressure refrigerant-cooling liquid heat exchanger is connected with the high-temperature cooling liquid loop and an indoor heater for heating in the passenger cabin through a fourth three-way water valve and a fifth three-way water valve, the battery is connected with the indoor cooler and the high-temperature cooling liquid loop through a sixth three-way water valve, and the second water pump is arranged between the high-pressure refrigerant-cooling liquid heat exchanger and the high-temperature cooling liquid loop;
the low-temperature coolant circuit includes: first expansion tank, driving motor, the heat dissipation water tank that has cooling fan, be used for promoting under the low temperature environment the temperature of low temperature heat source add hot water PTC and first water pump, wherein: the driving motor is connected with the heat dissipation water tank through a first three-way water valve, the heating water PTC and the low-pressure refrigerant-cooling liquid heat exchanger are connected through a first water pump, and the low-pressure refrigerant-cooling liquid heat exchanger is connected with the first expansion kettle and the low-temperature cooling liquid loop through a second three-way water valve.
2. The indirect low-temperature heat pump system as claimed in claim 1, wherein the electric compressor is an electric compressor with air supplement, and an air supplement VPI plate heat exchanger connected to an air supplement end of the electric compressor with air supplement is correspondingly arranged between the drying liquid storage tank and the low-pressure refrigerant-cooling liquid heat exchanger.
3. The heat exchange method of the indirect cryogenic heat pump system of claim 1 or 2, comprising: two kinds of refrigeration mode, seven heating modes, two kinds of refrigeration and heating demisting mode and heat dissipation water tank defrosting mode.
4. A heat exchange method according to claim 3, wherein the first of said two refrigeration modes is in particular: the high-temperature high-pressure gaseous refrigerant discharged from the electric compressor flows into the high-pressure refrigerant-cooling liquid heat exchanger for condensation and heat exchange, so that the effect of heating the cooling liquid on the other side of the heat exchanger is achieved; the condensed refrigerant flows out of the heat exchanger and enters the drying liquid storage tank to realize the gas-liquid separation effect, and the refrigerant flowing out of the liquid storage tank is ensured to be liquid; the refrigerant is divided into two parts at the outlet of the liquid storage tank: one path of refrigerant reaches an inlet of the air supplementing VPI electronic expansion valve along a branch, flows into one side of the air supplementing VPI plate heat exchanger after isenthalpic throttling to absorb heat, and flows out of the heat exchanger to reach an air supplementing port of the compressor to enter the compressor after the refrigerant which is changed into a medium-pressure overheat state flows out of the heat exchanger; the other path of refrigerant directly reaches the other side of the gas supplementing VPI plate type heat exchanger along the main path to release heat, the refrigerant which is changed into a high-pressure supercooled state flows out of the heat exchanger to reach the inlet of the main path electronic expansion valve, and the refrigerant flows into the low-pressure refrigerant-cooling liquid heat exchanger after isenthalpic throttling to evaporate and absorb heat so as to achieve the effect of cooling the cooling liquid on the other side of the heat exchanger; finally, the low-pressure superheated refrigerant flowing out of the heat exchanger returns to the suction port of the compressor to start the next cycle; in the mode, the cooling liquid loop can be divided into a high-temperature part and a low-temperature part according to the temperature of the cooling liquid, wherein the high-temperature cooling liquid loop is used for taking away heat released by condensation of a refrigerant in the heat exchanger and heat released by the driving motor; the low-temperature cooling liquid loop is used for conveying cooling liquid cooled by the heat exchanger to the indoor cooler so as to achieve the effect of cooling air in the carriage; in the high-temperature cooling liquid loop, cooling liquid cooled by the heat dissipation water tank reaches an inlet of the second water pump, the cooling liquid is sent into the heat exchanger by the water pump to absorb condensation heat emitted by the refrigerant on the other side, and the cooled cooling liquid returns to an inlet of the first expansion kettle through the fourth three-way water valve; the cooling liquid flowing out of the first expansion kettle reaches the inlet of the cooling module of the driving motor, the cooling liquid absorbs the heat dissipated by the driving motor to further raise the temperature, the high-temperature cooling liquid flows out of the driving motor, returns to the heat dissipation water tank through the first three-way water valve to be cooled and then starts the next circulation; in the low-temperature cooling liquid loop, after cooling liquid sent into the low-pressure refrigerant-cooling liquid heat exchanger by the first water pump is cooled by the refrigerant on the other side, the cooling liquid flows through the second three-way water valve to reach an inlet of the third three-way water valve, and all cooling liquid flowing out of the third three-way water valve flows into the indoor cooler to cool air flowing through the surface of fins of the indoor cooler, so that the effect of cooling a carriage is achieved; the heat-absorbed cooling liquid flows out of the indoor cooler and returns to the inlet of the first water pump through the heating water PTC to start the next circulation, and the heating water PTC does not work in the mode;
in the second refrigeration mode, the refrigerant loop and the high-temperature cooling liquid loop are consistent with the first refrigeration mode, only the cooling liquid flowing out of the third three-way water valve in the low-temperature cooling liquid loop needs to flow into the cooling module of the battery by part of the cooling liquid according to the thermal load of the battery, and the rest of the cooling liquid flows into the indoor cooler, so that the effect of refrigerating the battery and the compartment at the same time is achieved.
5. A heat exchange method according to claim 3 wherein one of said seven heating modes
In the first heating mode, the refrigerant circuit is consistent with the cooling mode, and only the high-temperature circuit and the low-temperature circuit of the cooling liquid need to be reorganized; in the low-temperature cooling liquid loop, the heat of the cooling liquid sent into the low-pressure refrigerant-cooling liquid heat exchanger by the first water pump is absorbed by the refrigerant on the other side, and then the temperature is reduced, and the low-temperature cooling liquid flows to the inlet of the first expansion kettle through the second three-way water valve; the cooling liquid flowing out of the first expansion kettle reaches the inlet of a cooling module of the driving motor, and the mode is suitable for an idling mode of the vehicle, so that the heat of the motor is less, and the temperature rise of the cooling liquid is small; cooling liquid flowing out of the driving motor returns to the inlet of the radiating water tank through the first three-way water valve, the temperature of the cooling liquid absorbing air blown across the surface of the fins of the water tank is increased, the heated cooling liquid flows through the heating water PTC and returns to the inlet of the first water pump to start the next circulation, and the heating water PTC does not work in the mode;
in the high-temperature cooling liquid loop, cooling liquid sent into the high-pressure refrigerant-cooling liquid heat exchanger through the second water pump absorbs condensation heat of a refrigerant on the other side of the heat exchanger, and the heated cooling liquid reaches an inlet of a fifth three-way water valve through a fourth three-way water valve; the cooling liquid flowing out of the fifth three-way water valve flows into the indoor heater completely, so that the temperature of the air flowing through the surface of the fins of the indoor heater is raised, the heating effect of the compartment is achieved, and the cooling liquid after heat release flows out of the indoor heater and then returns to the inlet of the second water pump to start the next circulation;
in the second heating mode, the refrigerant loop and the low-temperature cooling liquid loop are consistent with the first heating mode, only the cooling liquid flowing out of the fifth three-way water valve in the high-temperature cooling liquid loop needs to be divided into a part of cooling liquid to flow into the cooling module of the battery according to the heating requirement of the battery, and the rest of the cooling liquid flows into the indoor heater, so that the effect of heating the battery and the compartment at the same time is achieved;
in the third heating mode, the refrigerant loop and the high-temperature cooling liquid loop are consistent with the first heating mode, but low-temperature cooling liquid flowing out of the second three-way water valve needs to be divided into one path and flows into the cooling module of the battery through the second expansion kettle and the third three-way water valve, and the waste heat of the battery is absorbed and utilized as a second low-temperature heat source; the cooling liquid flowing out of the battery passes through a sixth three-way water valve and then is mixed with the cooling liquid flowing out of the heat dissipation water tank, the cooling liquid returns to the inlet of the first water pump through the heating water PTC to start the next circulation, and the heating water PTC does not work in the mode;
in the fourth heating mode, the refrigerant loop and the high-temperature cooling liquid loop are consistent with the second heating mode, but the low-temperature heat source of the heat pump in the low-temperature cooling liquid loop is different, and the mode is suitable for the running working condition and absorbs the heat dissipating capacity of the motor to complete the heat pump circulation; the low-temperature cooling liquid flows through the second three-way water valve to reach the inlet of the first expansion kettle, the cooling liquid flowing out of the first expansion kettle reaches the inlet of the cooling module of the driving motor, the motor is in high-speed operation at the moment, the heat dissipation capacity is large, and the temperature rise of the cooling liquid is large after flowing through the driving motor; the cooling liquid flowing out of the driving motor bypasses the heat dissipation water tank through the first three-way water valve, does not exchange heat with the external environment, flows through the heating water PTC and returns to the inlet of the first water pump to start the next circulation, and the heating water PTC does not work in the mode;
in the fifth heating mode, the schematic diagram of the system is consistent with that of the fourth heating mode, but at the moment, the PTC (positive temperature coefficient) heating water starts to work to provide a low-temperature heat source, and the low-temperature cooling liquid loop does not exchange heat with the external environment, so that the heat pump can still normally operate at a lower environmental temperature;
in the sixth heating mode, the refrigerant circuit is consistent with the fourth heating mode, but the high-temperature circuit and the low-temperature circuit of the cooling liquid need to be reorganized; in the low-temperature cooling liquid loop, low-temperature cooling liquid flowing out of the second three-way water valve needs to be divided into one path, flows into a cooling module of the battery through the second expansion kettle and the third three-way water valve, and absorbs and utilizes the waste heat of the battery as a second low-temperature heat source; the cooling liquid flowing out of the battery is mixed with the cooling liquid flowing out of the heat dissipation water tank after passing through a sixth three-way water valve, and returns to the inlet of the first water pump through the heating water PTC to start the next cycle, and the heating water PTC does not work in the mode; correspondingly, in the high-temperature cooling liquid loop, all the cooling liquid flowing out of the fifth three-way water valve flows into the indoor heater heating compartment, and the water loop of the high-temperature cooling liquid flowing into the battery is cut off;
the seventh heating mode is used for directly heating the carriage by using the heat of the motor when the heating demand of the carriage is not large, and the refrigerant loop does not work at the moment; the cooling liquid flows through the heat exchanger from the outlet of the second water pump and then reaches the inlet of the fourth three-way water valve, and the outlet of the fourth three-way water valve is divided into two parts: one path of cooling liquid completely flows into the indoor heater through a fifth three-way water valve to heat air blown on the surfaces of fins of the indoor heater, so that the effect of heating a carriage is achieved; and the other path of cooling liquid absorbs the heat released by the driving motor after flowing through the first expansion kettle, and returns to the inlet of the second water pump to join with the low-temperature cooling liquid at the outlet of the indoor heater by utilizing the bypass of the first three-way water valve without passing through the heat dissipation water tank, so that the temperature of the mixed cooling liquid is increased and the next circulation is started.
6. The heat exchange method as set forth in claim 3, wherein in the two cooling and heating demisting modes,
the first refrigerating and heating demisting mode is used for the working condition that the compartment has refrigerating and dehumidifying requirements and heating and warming requirements at the same time, the refrigerant loop and the low-temperature cooling liquid loop are kept consistent with the first refrigerating mode in the first refrigerating mode, and compared with the high-temperature cooling liquid loop in the first refrigerating mode, the mode divides the outlet cooling liquid of the fourth three-way water valve into two parts, introduces one path of high-temperature cooling liquid to flow into the indoor heater to heat the compartment, and meets the requirement of heating and warming the compartment;
the second refrigerating and heating demisting mode is used for the working condition that the carriage has larger heating and temperature rising requirements, and the refrigerant loop and the low-temperature cooling liquid loop are kept consistent with the first refrigerating and heating demisting mode in the mode; in the high-temperature cooling liquid loop, the low-temperature cooling liquid returns to the inlet of the second water pump and is converged with the low-temperature cooling liquid at the outlet of the indoor heater by using a first three-way water valve bypass without passing through the radiating water tank; the high-temperature heat is not released to the environment through the heat dissipation water tank at the moment, the temperature of the cooling liquid entering the second water pump after mixing can be further improved, and therefore the requirement of a larger heating temperature rise of the carriage is met.
7. The heat exchange method as claimed in claim 3, wherein in the defrosting mode of the radiator tank,
the cooling water tank defrosting mode is used for a scene of defrosting the cooling water tank by using the heating capacity of the heat pump, and a refrigerant circuit is consistent with a refrigeration mode in the mode; in the high-temperature cooling liquid loop, cooling liquid sent into the high-pressure refrigerant-cooling liquid heat exchanger through the second water pump absorbs condensation heat of a refrigerant on the other side of the heat exchanger, and the heated cooling liquid reaches an inlet of the first expansion kettle through the fourth three-way water valve; the cooling liquid flowing out of the first expansion kettle reaches the inlet of the cooling module of the driving motor, the cooling liquid absorbs the heat dissipated by the driving motor to further raise the temperature, the high-temperature cooling liquid flows out of the driving motor, returns to the heat dissipation water tank through the first three-way water valve to dissipate heat and defrost, and returns to the inlet of the second water pump to start the next circulation;
in the low-temperature cooling liquid loop, the cooling liquid heat sent into the low-pressure refrigerant-cooling liquid heat exchanger by the first water pump is absorbed by the refrigerant on the other side, then the temperature is reduced, the low-temperature cooling liquid flows to the second expansion kettle through the second three-way water valve, flows into the cooling module of the battery through the second expansion kettle and the third three-way water valve, and absorbs and utilizes the waste heat of the battery as a low-temperature heat source; the cooling liquid flowing out of the battery returns to the inlet of the first water pump through the sixth three-way water valve and the heating water PTC to start the next circulation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010999997.1A CN112208295B (en) | 2020-09-22 | 2020-09-22 | Indirect low-temperature heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010999997.1A CN112208295B (en) | 2020-09-22 | 2020-09-22 | Indirect low-temperature heat pump system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112208295A CN112208295A (en) | 2021-01-12 |
| CN112208295B true CN112208295B (en) | 2023-01-20 |
Family
ID=74049092
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010999997.1A Active CN112208295B (en) | 2020-09-22 | 2020-09-22 | Indirect low-temperature heat pump system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112208295B (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113276623B (en) * | 2021-05-27 | 2022-03-01 | 东风汽车集团股份有限公司 | Double-expansion-water-tank heat management system of hybrid electric vehicle and control method thereof |
| CN113237145B (en) * | 2021-05-27 | 2022-05-20 | 深圳昂湃技术有限公司 | Heat pump air conditioning device and implementation method thereof |
| CN113386527B (en) * | 2021-07-30 | 2022-05-03 | 重庆长安新能源汽车科技有限公司 | Thermal management system and control method of pure electric vehicle and pure electric vehicle |
| CN113547890B (en) * | 2021-07-30 | 2022-05-03 | 重庆长安新能源汽车科技有限公司 | Thermal management system, thermal management system control method and automobile |
| CN113400894B (en) * | 2021-07-30 | 2022-10-04 | 重庆长安新能源汽车科技有限公司 | Automobile small-sized air conditioner box assembly, automobile air conditioner control method and automobile |
| CN113386526B (en) * | 2021-07-30 | 2022-06-14 | 重庆长安新能源汽车科技有限公司 | Indirect heat pump air conditioning system, control method and pure electric vehicle |
| CN114103592B (en) * | 2021-11-22 | 2023-11-21 | 泉州装备制造研究所 | Movable container type heat pump drying system, transport vehicle and drying method |
| CN114228441A (en) * | 2022-01-13 | 2022-03-25 | 大连旋科企业管理合伙企业(有限合伙) | Modularized comprehensive heat management system for new energy vehicle |
| CN114427758B (en) * | 2022-01-28 | 2023-04-28 | 内蒙古中电储能技术有限公司 | Solar energy supply system and working method thereof |
| CN114963613A (en) * | 2022-05-23 | 2022-08-30 | 富奥汽车零部件股份有限公司 | Heat pump system and car |
| CN115626030B (en) * | 2022-11-18 | 2023-03-21 | 小米汽车科技有限公司 | Thermal management system and vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104235978A (en) * | 2014-08-22 | 2014-12-24 | 海信（山东）空调有限公司 | Cold storage and heat storage type air conditioner |
| CN107512150A (en) * | 2017-09-13 | 2017-12-26 | 艾泰斯热系统研发（上海）有限公司 | Electric automobile heat-pump air-conditioning system |
| CN110108055A (en) * | 2018-02-01 | 2019-08-09 | 上海银轮热交换系统有限公司 | The heat pump integrated system of car air-conditioner |
| CN110641248A (en) * | 2019-10-28 | 2020-01-03 | 湖北文理学院 | Fuel cell automobile heat pump air conditioning system, control method and air conditioner |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108482064B (en) * | 2018-04-18 | 2023-07-14 | 上海加冷松芝汽车空调股份有限公司 | Integrated passenger cabin air conditioner and battery pack thermal management heat pump system for new energy vehicle |
| DE102020100428A1 (en) * | 2019-02-06 | 2020-08-06 | Hanon Systems | Air conditioning and battery cooling arrangement with high cooling capacity and passive battery cooling and method for operating an air conditioning and battery cooling arrangement |
| CN109941065A (en) * | 2019-04-11 | 2019-06-28 | 上海理工大学 | Biquadratic circuit Gas-supplying enthalpy-increasing electric automobile air conditioner heat pump system |
-
2020
- 2020-09-22 CN CN202010999997.1A patent/CN112208295B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104235978A (en) * | 2014-08-22 | 2014-12-24 | 海信（山东）空调有限公司 | Cold storage and heat storage type air conditioner |
| CN107512150A (en) * | 2017-09-13 | 2017-12-26 | 艾泰斯热系统研发（上海）有限公司 | Electric automobile heat-pump air-conditioning system |
| CN110108055A (en) * | 2018-02-01 | 2019-08-09 | 上海银轮热交换系统有限公司 | The heat pump integrated system of car air-conditioner |
| CN110641248A (en) * | 2019-10-28 | 2020-01-03 | 湖北文理学院 | Fuel cell automobile heat pump air conditioning system, control method and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112208295A (en) | 2021-01-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN112208295B (en) | Indirect low-temperature heat pump system | |
| CN102563943B (en) | The refrigerant circulation loop of air conditioning equipment of car | |
| CN108973587B (en) | Automobile heat pump air conditioning system and control method | |
| US6722147B2 (en) | Coolant circuit of a motor vehicle having a coolant/refrigerant heat exchanger | |
| CN112428767B (en) | Vehicle thermal management system | |
| CN110435390A (en) | A kind of thermal management system of whole suitable for new-energy automobile under worst cold case | |
| US11752833B2 (en) | System for air-conditioning the air of a passenger compartment and for heat transfer with drive components of a motor vehicle and method for operating the system | |
| CN113173050B (en) | Thermal management system | |
| CN109760484B (en) | Electric automobile thermal management system | |
| US10611212B2 (en) | Air conditioner for vehicle | |
| CN112248743A (en) | Dual-temperature-zone outdoor heat exchanger heat pump system | |
| CN109849617B (en) | Thermal management system for electric automobile | |
| CN113173049B (en) | Thermal management system | |
| US20230339293A1 (en) | System for air-conditioning the air of a passenger compartment and for heat transfer by way of components of a powertrain of a motor vehicle, as well as method for operating the system | |
| KR20190103009A (en) | Device for an air-conditioning system of a motor vehicle and method for operating the device | |
| CN110356283B (en) | Thermal management system of vehicle power battery | |
| CN115416444A (en) | Heat pump heat management system for new energy automobile and working method of heat pump heat management system | |
| KR20180122289A (en) | Device for an air conditioning system of a motor vehicle and method for operating the device | |
| CN212194994U (en) | Vehicle thermal management system | |
| JP2012111251A (en) | Air conditioner for vehicle | |
| CN215284271U (en) | New energy hybrid vehicle type cab and power battery integrated thermal management system | |
| CN115716395A (en) | Thermal management system and thermal management method for electric vehicle and electric vehicle | |
| CN206765743U (en) | Heat pump, heat pump and electric automobile for vehicle | |
| CN114407604A (en) | Integrated electric automobile thermal management system, control method and electric automobile | |
| CN114834214A (en) | Air conditioning system for a motor vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |