CN113715574B - Transcritical carbon dioxide electric automobile thermal management system and frostless control method thereof - Google Patents
Transcritical carbon dioxide electric automobile thermal management system and frostless control method thereof Download PDFInfo
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- CN113715574B CN113715574B CN202110865519.6A CN202110865519A CN113715574B CN 113715574 B CN113715574 B CN 113715574B CN 202110865519 A CN202110865519 A CN 202110865519A CN 113715574 B CN113715574 B CN 113715574B
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- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 title claims abstract description 54
- 238000000034 method Methods 0.000 title claims abstract description 42
- 229910002092 carbon dioxide Inorganic materials 0.000 title claims abstract description 27
- 239000001569 carbon dioxide Substances 0.000 title claims abstract description 26
- 238000010438 heat treatment Methods 0.000 claims abstract description 78
- 239000007788 liquid Substances 0.000 claims abstract description 21
- 238000010257 thawing Methods 0.000 claims abstract description 14
- 239000003507 refrigerant Substances 0.000 claims description 45
- 238000001704 evaporation Methods 0.000 claims description 29
- 230000007613 environmental effect Effects 0.000 claims description 22
- 230000008020 evaporation Effects 0.000 claims description 16
- 238000013459 approach Methods 0.000 claims description 15
- 230000000704 physical effect Effects 0.000 claims description 9
- 230000033228 biological regulation Effects 0.000 claims description 7
- 230000001172 regenerating effect Effects 0.000 claims description 5
- 230000002238 attenuated effect Effects 0.000 abstract description 4
- 230000002457 bidirectional effect Effects 0.000 abstract 1
- 230000007423 decrease Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000008929 regeneration Effects 0.000 description 2
- 238000011069 regeneration method Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- 102100040359 Angiomotin-like protein 2 Human genes 0.000 description 1
- 101000891151 Homo sapiens Angiomotin-like protein 2 Proteins 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 230000035800 maturation Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00735—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models
- B60H1/00807—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models the input being a specific way of measuring or calculating an air or coolant temperature
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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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00735—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models
- B60H1/00785—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models by the detection of humidity or frost
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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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
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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
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
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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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00961—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising means for defrosting outside heat exchangers
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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
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
- B60H2001/2268—Constructional features
- B60H2001/2281—Air supply, exhaust systems
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- Thermal Sciences (AREA)
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention belongs to the technical field of carbon dioxide systems, and discloses a transcritical carbon dioxide electric automobile thermal management system and a frostless control method thereof, wherein the system comprises the following components: the outlet of the compressor is connected with the inlet of the defrosting heat exchanger, the outlet of the defrosting heat exchanger is connected with the inlet of the main heat exchanger through a full-through throttle valve, the outlet of the second four-way heat exchange valve is connected with the outlet of the main heat exchanger, the outlet of the second four-way heat exchange valve is connected with the outlet of the heat regenerator through a bidirectional throttle valve, the outlet of the second four-way heat exchange valve is connected with the inlet of the outdoor heat exchanger, the outlet of the outdoor heat exchanger is connected with the outlet of the first four-way reversing valve, the outlet of the first four-way reversing valve is connected with the inlet of the gas-liquid separator, the outlet of the gas-liquid separator is connected with the outlet of the heat regenerator, and the outlet of the heat regenerator is connected with the inlet of the compressor. A frostless control method under each working condition is also provided. The invention can realize frostless operation, and the heating performance is not easy to be seriously attenuated; and the thermal management system has simple architecture and low cost.
Description
Technical Field
The invention belongs to the technical field of transcritical carbon dioxide systems, and particularly relates to a transcritical carbon dioxide electric automobile thermal management system and a frostless control method thereof.
Background
The heat pump system can recycle the environment and waste heat back to the heating process, and has the advantages of high efficiency and energy conservation. Scientists and scholars have made many efforts to alleviate the shortage of energy and the aggravation of environmental pollution, and the gradual maturation of the related art of electric vehicles and the popularization of electric vehicles are one of representative measures. However, other potential hazards associated with electric vehicles are increasingly being discovered. For example, the refrigerant is insufficiently heated in winter, and a positive temperature coefficient thermistor is usually requiredPositive Temperature Coefficient, PTC for short) to assist in heating the cabin, a large amount of battery power is consumed, resulting in a sudden decrease in driving range of the electric vehicle. Development of an independent heat pump system is critical to popularization of electric automobiles. Since 1 in 2017, 1, the use of refrigerants with global warming potential (Global Warming Potential, GWP for short) higher than 150 is prohibited, and R134a (1, 2-tetrafluoroethane) is gradually eliminated. Finding new natural and environmentally friendly alternative refrigerants is a current new research hotspot. CO 2 The service life of the refrigerant is 18-49% lower than that of R134a (Life Cycle Climate Performance, LCCP for short), and CO2 is used as a natural refrigerant, has the advantages of environmental friendliness, low cost, excellent heating performance and the like, and becomes one of the most ideal refrigerants for heating the automobile air conditioner in winter.
However, at low temperature heating, the biggest potential performance hazard for refrigeration systems is that the evaporator surfaces may frost when the evaporation temperature is below the dew point temperature of the air. Frosting on the evaporator surface increases the heat exchange resistance and windage resistance of the refrigerant and air in the evaporator. As the thickness of the frost layer increases, the heat transfer performance gradually decreases. Leading to rapid deterioration of the heating amount, it is very important to study defrosting for improving the performance of the winter heating system. This disadvantage severely hampers transcritical CO 2 The advancing pace of the development of the green refrigerant is tired.
Disclosure of Invention
The invention aims to provide a transcritical carbon dioxide electric automobile thermal management system and a frostless control method thereof so as to solve the problem of CO 2 When the natural refrigerant is used as a natural refrigerant, heat exchange thermal resistance and wind resistance of the refrigerant and air in the evaporator can be increased due to frosting on the surface of the evaporator; as the thickness of the frost layer increases, the heat transfer performance gradually decreases, resulting in a technical problem that the heating amount rapidly deteriorates.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
a transcritical carbon dioxide electric vehicle thermal management system comprising: the system comprises a compressor, a first four-way reversing valve, a defrosting heat exchanger, a main heat exchanger, an indoor fan, a second four-way reversing valve, a heat regenerator, an outdoor heat exchanger and a gas-liquid separator;
the outlet of the compressor is connected with an a port of the first four-way reversing valve, a b port of the first four-way reversing valve is connected with an inlet of the defrosting heat exchanger, an outlet of the defrosting heat exchanger is connected with an inlet of the main heat exchanger through an all-way throttle valve, an a port of the second four-way reversing valve is connected with an outlet of the main heat exchanger, a c port of the second four-way reversing valve is connected with a d port of the regenerator through a two-way throttle valve, a c port of the regenerator is connected with a b port of the second four-way reversing valve, a d port of the second four-way reversing valve is connected with an inlet of the outdoor heat exchanger, an outlet of the outdoor heat exchanger is connected with a d port of the first four-way reversing valve, a c port of the first four-way reversing valve is connected with an inlet of the gas-liquid separator, an outlet of the gas-liquid separator is connected with a b port of the regenerator, and an a port of the regenerator is connected with an inlet of the compressor; the port a of the heat regenerator is communicated with the port b of the heat regenerator; the c port of the heat regenerator is communicated with the d port of the heat regenerator.
The invention is further improved in that: an outdoor fan is arranged beside the outdoor heat exchanger; an outdoor thermometer and an outdoor hygrometer are arranged at the outdoor heat exchanger.
The frostless control method of the transcritical carbon dioxide electric automobile heat management system comprises the following steps: the method comprises the steps of collecting the ambient temperature and the relative humidity, and controlling the working mode of the transcritical carbon dioxide electric automobile thermal management system according to the ambient temperature and the relative humidity:
(1) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env not less than 5, or
T env <5，T dew ＝f(T env ,H env )，T env -T dew ≥N
Wherein T is dew N=5 for dew point temperature;
at the moment, the transcritical carbon dioxide electric automobile heat management system is controlled to operate in a conventional heating mode under the conventional heating working condition;
(2) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env <at 5, T dew ＝f(T env ,H env )，M<T env -T dew <N,
N＝5，M＝3.5；
At the moment, the trans-critical carbon dioxide electric automobile heat management system is controlled to operate in one of a conventional heating mode or a frostless control mode with low heating quantity requirement under the light frosting working condition;
(3) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
Q<T env <at 5, T dew ＝f(T env ,H env )，T env -T dew <M
Q＝-10；
At the moment, the trans-critical carbon dioxide electric automobile heat management system is controlled to operate in a frostless control mode with low heating quantity requirement under the severe frosting working condition with low heating quantity requirement;
(4) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env when Q is less than or equal to Q, T dew ＝f(T env ,H env )，T env -T dew <M
And controlling the transcritical carbon dioxide electric automobile thermal management system to operate in a frostless control mode with high heating requirements under the severe frosting working condition with high heating requirements.
The invention is further improved in that: during the conventional heating mode, the ab channel of the first four-way reversing valve is controlled to be communicated, the cd channel is controlled to be communicated, the ac channel of the second four-way reversing valve is connected, the bd channel is connected, the regenerator is in a small regenerative working mode, and the refrigerant after the two-way throttle valve exchanges heat with the refrigerant at the outlet of the gas-liquid separator, so that the heat exchange quantity is minimum.
The invention is further improved in that: when the thermal management system is in a conventional heating mode, the air supply quantity of the carriage is controlled by the rotating speed of the indoor fan, the air supply temperature of the carriage is controlled by the rotating speed of the compressor, and the optimal exhaust pressure value exists in the thermal management system so that the power consumption of the compressor is minimized when heat is customized; the exhaust pressure of the heat management system is controlled by the opening degree of the two-way throttle valve, the air quantity of the outdoor heat exchanger is controlled by the rotating speed of the outdoor fan, and the air quantity of the outdoor heat exchanger is controlled by the rotating speed of the outdoor fanIn the thermal management system under thermal operation, the optimal exhaust pressure P opt And ambient temperature T env Air inlet temperature T of carriage air And the air supply temperature T of the carriage sup Correlation: p (P) opt ＝f(T env ,T air ,T sup )。
The invention is further improved in that: and when the frostless control mode with low heating capacity is required, the ab channel of the first four-way reversing valve is controlled to be communicated, the cd channel is controlled to be communicated, the ab channel of the second four-way reversing valve is connected, the cd channel is connected, the regenerator is in a large-regenerative working mode, the refrigerant at the outlet of the main heat exchanger exchanges heat with the refrigerant at the outlet of the gas-liquid separator, and the heat exchange capacity is larger than that in the conventional heating mode.
The invention is further improved in that: when the thermal management system is in a frostless control mode with low heating capacity requirement, the thermal management system is used for customizing heat operation under performance loss, frostless control is started, the air supply quantity of a carriage is controlled by the rotating speed of an indoor fan, the air supply temperature of the carriage is controlled by the rotating speed of a compressor, the evaporation temperature is judged in real time, meanwhile, the opening degree of an all-pass throttle valve is used for controlling a high-pressure value to approach an optimal exhaust pressure value in real time, and the target value T of the evaporation temperature is calculated according to the control value T eva0 The method is determined by the ambient temperature and humidity, and comprises the following specific steps:
the first step: the temperature and humidity values of the environment are measured by an outdoor thermometer and an outdoor hygrometer and respectively recorded as T env And H env ；
And a second step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env )；
Third step, the evaporating temperature T of the refrigerant is collected eva Air supply temperature T of carriage sup Exhaust pressure value P dis Target set value T of carriage air supply temperature set by passenger or manufacturer sup-aim ；
Fourth, control and regulate to start, the compressor starts at the initial set rotation speed, when T eva >T dwe -1, increasing the rotational speed of the compressor to raise the supply air temperature while reducingThe opening of the small full-through throttle valve enables the exhaust pressure value to approach the optimal exhaust pressure value, the evaporation temperature is judged once every 10s, and when the evaporation temperature meets T eva <T dwe At the time of-1, starting to increase the opening of the all-pass throttle valve until T eva ＝T dwe -1 and T sup ＝T sup-aim At this time, the pressure difference between the real-time exhaust pressure value and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation of the outdoor heat exchanger, so that the performance loss of the thermal management system is minimum.
The invention is further improved in that: and when the frostless control mode with high heating capacity requirement is adopted, the ab channel of the first four-way reversing valve is controlled to be communicated, the cd channel is controlled to be communicated, the ab channel of the second four-way reversing valve is connected, the cd channel is connected, the regenerator is in a large regenerative working mode, and the refrigerant at the outlet of the main heat exchanger exchanges heat with the refrigerant at the outlet of the gas-liquid separator, so that the heat exchange capacity is maximum.
The invention is further improved in that: when the thermal management system is in a frostless control mode with high heating requirement, the air supply quantity of the carriage is controlled by the rotating speed of the indoor fan, the air supply temperature of the carriage is controlled by the rotating speed of the compressor, the temperature of the refrigerant at the outlet of the evaporator is judged in real time, and meanwhile, the opening degree of the all-pass throttle valve is used for controlling the high-pressure value to approach the optimal exhaust pressure value in real time, wherein the target value T of the temperature of the refrigerant at the outlet of the evaporator eva-out0 The method is determined by the ambient temperature and humidity, and comprises the following specific steps:
the first step: the temperature and humidity values of the environment are measured by an outdoor thermometer and an outdoor hygrometer and respectively recorded as T env And H env ；
And a second step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env )；
Third step, collecting the refrigerant temperature T of the evaporator outlet of the refrigerant eva-out Air supply temperature T of carriage sup Exhaust pressure value P dis ；
Fourth, controlling and adjusting to start, and starting the compressor at the initial set rotating speedWhen T eva-out >T dwe When in process of-1, increasing the rotating speed of the compressor to increase the air supply temperature, simultaneously reducing the opening of the all-pass throttle valve to enable the exhaust pressure value to approach the optimal exhaust pressure value, judging the evaporation temperature once every 10s, and when the evaporation temperature meets T eva-out <T dwe At the time of-1, starting to increase the opening of the all-pass throttle valve until T eva-out ＝T dwe -1 and T sup ＝T sup-aim At this time, the pressure difference between the real-time exhaust pressure value and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation of the outdoor heat exchanger, so that the performance loss of the thermal management system is minimum.
The invention is further improved in that: when the environmental working condition is in a frosting working condition (except the first conventional heating working condition, the other three working conditions are frosting working conditions), and when the thermal management system is started once, the thermal management system is operated for customizing heat loss, and the control system starts a frostless control mode; when the secondary starting is performed, a secondary starting frostless control mode is adopted, the air supply quantity and the air supply temperature set value of the carriage are set values, the set value gear is selected automatically, the air supply quantity of the carriage is controlled by the rotating speed of the indoor fan, the air supply temperature of the carriage is controlled by the rotating speed of the compressor, and the specific determining steps are as follows:
the first step: the temperature of the environment is measured by an outdoor thermometer and an outdoor hygrometer and is marked as T env ；
And a second step of: the maximum humidity corresponding to the temperature is H env-max ；
And a third step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env-max )；
Fourth, control and regulation are started, the compressor is started at the initial set rotation speed, and when T is the time eva >T dwe When in process of-1, increasing the rotating speed of the compressor to increase the air supply temperature, simultaneously reducing the opening of the all-pass throttle valve to enable the exhaust pressure value to approach the optimal exhaust pressure value, judging the evaporation temperature once every 10s, and when the evaporation temperature meets T eva <T dwe At the time of-1, the opening degree of the all-pass throttle valve starts to be increased untilT eva ＝T dwe -1 and T sup ＝T sup-aim The pressure difference between the real-time value of the exhaust pressure and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation condition of the evaporator, so that the performance loss of the thermal management system is minimum.
Compared with the prior art, the invention has the following beneficial effects:
1. the invention can realize frostless operation, and the heating performance can not be seriously attenuated after the air conditioner is operated for a long time;
2. the thermal management system has simple structure and low cost, and the control method is simple and convenient.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
FIG. 1 is a cycle chart of a conventional heating mode of a transcritical carbon dioxide electric vehicle thermal management system of the present invention;
fig. 2 is a schematic diagram of a large regenerative frost-free control mode of a regenerator of a transcritical carbon dioxide electric vehicle thermal management system of the invention.
In the figure: 1. a compressor; 2. a first four-way reversing valve; 3. a defrosting heat exchanger; 4. an all-pass throttle valve; 5. a main heat exchanger; 6. an indoor fan; 7. a second four-way reversing valve; 8. a regenerator; 9. a two-way throttle valve; 10. an outdoor heat exchanger; 11 a gas-liquid separator; 12. an outdoor fan.
Detailed Description
The invention will be described in detail below with reference to the drawings in connection with embodiments. It should be noted that, without conflict, the embodiments of the present invention and features of the embodiments may be combined with each other.
The following detailed description is exemplary and is intended to provide further details of the invention. Unless defined otherwise, all technical terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the invention.
It will be appreciated by those skilled in the art that the present invention can be carried out in other embodiments without departing from the spirit or essential characteristics thereof. Accordingly, the above disclosed embodiments are illustrative in all respects, and not exclusive. All changes that come within the scope of the invention or equivalents thereto are intended to be embraced therein.
Example 1
Referring to fig. 1 and 2, the present invention provides a transcritical carbon dioxide electric automobile thermal management system, comprising: the air conditioner comprises a compressor 1, a first four-way reversing valve 2, a defrosting heat exchanger 3, an all-way throttle valve 4, a main heat exchanger 5, an indoor fan 6, a second four-way reversing valve 7, a heat regenerator 8, a two-way throttle valve 9, an outdoor heat exchanger 10, a gas-liquid separator 11, an outdoor fan 12, an outdoor thermometer 13 and an outdoor hygrometer 14.
The heat management system comprises an outdoor heat exchange system and an indoor heat exchange system;
an outlet of the compressor 1 is connected with an a port of the first four-way reversing valve 2, a b port of the first four-way reversing valve 2 is connected with an inlet of the defrosting heat exchanger 3, and an outlet of the defrosting heat exchanger 3 is connected with an inlet of the main heat exchanger 5 through the all-way throttle valve 4. The port a of the second four-way heat exchange valve 7 is connected with the outlet of the main heat exchanger 5, the port c of the second four-way reversing valve 7 is connected with the port d of the heat regenerator 8 through a two-way throttle valve 9, the port c of the heat regenerator 8 is connected with the port b of the second four-way reversing valve 7, the port d of the second four-way reversing valve 7 is connected with the inlet of the outdoor heat exchanger 10, the outlet of the outdoor heat exchanger 10 is connected with the port d of the first four-way reversing valve 2, the port c of the first four-way reversing valve 2 is connected with the inlet of the gas-liquid separator 11, the outlet of the gas-liquid separator 11 is connected with the port b of the heat regenerator 8, and the port a of the heat regenerator 8 is connected with the inlet of the compressor 1;
the outdoor heat exchange system includes: an outdoor heat exchanger 10, an outdoor fan 12, an outdoor thermometer 13 and an outdoor hygrometer 14; the outdoor heat exchanger 10 exchanges heat through an outdoor fan 12, and an outdoor thermometer 13 and an outdoor hygrometer 14 are arranged in the outdoor heat exchanger 10 and are respectively used for measuring the temperature and the humidity of the environment; the indoor heat exchange system includes: defrost heat exchanger 3, main heat exchanger 5 and indoor fan 6.
The transcritical carbon dioxide electric automobile thermal management system can divide the operation working conditions into four types according to the ambient temperature and the ambient humidity: conventional heating working conditions, mild frosting working conditions, low heating quantity required heavy frosting working conditions and high heating quantity heavy frosting working conditions;
(1) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env not less than 5 or
T env <5，T dew ＝f(T env ,H env )，T env -T dew ≥N
Wherein T is dew The recommended value of N is 5 for dew point temperature;
at this time, the conventional heating working condition is adopted, and the thermal management system is in a conventional heating mode;
(2) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env <at 5, T dew ＝f(T env ,H env )，M<T env -T dew <N,
The recommended value of N is 5, and the recommended value of M is 3.5;
at the moment, the operation mode of the thermal management system is related to the operation time of the thermal management system under the light frosting working condition, and the thermal management system can adopt one of a conventional heating mode or a frostless control mode with low heating quantity requirement;
(3) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
Q<T env <at 5, T dew ＝f(T env ,H env )，T env -T dew <M
The recommended value of Q is-10, and the recommended value of M is 3.5;
at the moment, the heat exchanger is rapidly frosted under the working condition of low heating demand severe frosting, the heating quantity is seriously attenuated, and the thermal management system adopts a frostless control mode with low heating quantity demand:
(4) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env when Q is less than or equal to Q, T dew ＝f(T env ,H env )，T env -T dew <M
The recommended value of Q is-10, and the recommended value of M is 3.5;
at the moment, the frosting speed of the heat exchanger is the fastest and the heating quantity is seriously attenuated under the working condition of heavy frosting with high heating demands, and the frostless control mode with the high heating demands of the thermal management system is adopted.
The three control modes of the thermal management system are respectively as follows: a conventional heating mode, a low heating amount demand frostless control mode and a high heating amount demand frostless control mode:
(1) Referring to fig. 1, when the thermal management system is in the conventional heating mode, the influence of frost on the heating capacity of the thermal management system is small, the ab channel of the first four-way reversing valve 2 is connected, the cd channel is connected, the ac channel of the second four-way reversing valve 7 is connected, the bd channel is connected, the regenerator 8 is in the small regenerative mode, the refrigerant after the two-way throttle valve 9 exchanges heat with the refrigerant at the outlet of the gas-liquid separator 11, and the heat exchange capacity is minimum;
(2) Referring to fig. 2, when the thermal management system is in the frostless control mode with low heating capacity requirement, the ab channel of the first four-way reversing valve 2 is connected, the cd channel is connected, the ab channel of the second four-way reversing valve 7 is connected, the cd channel is connected, the regenerator 8 is in the large-regenerative mode, the refrigerant at the outlet of the main heat exchanger 5 exchanges heat with the refrigerant at the outlet of the gas-liquid separator 11, the two fluid temperature differences are large, and the heat exchange capacity is larger than that in the conventional heating mode;
(3) Referring to fig. 2, when the thermal management system is in the frostless control mode with high heating capacity requirement, the ab channel of the first four-way reversing valve 2 is connected, the cd channel is connected, the ab channel of the second four-way reversing valve 7 is connected, the regenerator 8 is in the large-regenerative mode, the refrigerant at the outlet of the main heat exchanger 5 exchanges heat with the refrigerant at the outlet of the gas-liquid separator 11, the two fluid flows have large temperature difference, and the heat exchange capacity is maximum.
The control mode of the thermal management system of the light frosting working condition is related to the operation time t of the thermal management system during running, and three conditions exist:
(1) When t is less than or equal to Pmin and the recommended value of P is 60, the air conditioning system is in a conventional heating mode, and the influence of frosting on the heating capacity of the air conditioning system is small;
(2) After the vehicle starts navigation, acquiring navigation time information and road condition information, and adopting a frostless control mode when the driving operation time exceeds Pmin;
(3) When the vehicle is not started for navigation, navigation time information and road condition information cannot be acquired, driving operation time is not obtained, and at the moment, the influence of the operation time is not considered, and the low heating capacity demand frostless control mode or the high heating capacity demand frostless control mode is only judged through the ambient temperature and the ambient humidity.
The function of the heat regenerator 8 comprises a small heat regeneration function of a conventional heating mode, a large heat regeneration function of a frostless control mode with low heating capacity requirement and a frostless control mode with high heating capacity requirement.
Example 2
The invention provides a frostless control method of a transcritical carbon dioxide electric automobile thermal management system, which comprises the following steps:
(1) Control method of conventional heating mode
When the thermal management system is in the conventional heating mode, the thermal management system operates by customizing heat for optimal performance, the air supply volume and the air supply temperature set values of the carriage are fixed values, the set value gear can be selected independently, the air supply volume of the carriage is controlled by the rotating speed of the indoor fan 6, the air supply temperature of the carriage is controlled by the rotating speed of the compressor 1, the thermal management system has an optimal exhaust pressure value to minimize the power consumption of the compressor 1 when customizing heat, therefore, the exhaust pressure of the thermal management system is controlled by the opening degree of the two-way throttle valve 9, the air volume of the outdoor heat exchanger 10 is controlled by the rotating speed of the outdoor fan 12, and the optimal exhaust pressure P of the thermal management system under the operation of customizing heat opt And ambient temperature T env Air inlet temperature T of carriage air And the air supply temperature T of the carriage sup Correlation: p (P) opt ＝f(T env ,T air ,T sup )；
(2) Control method of frostless control mode with low heating capacity requirement
When the thermal management system is in the frostless control mode with low heating capacity requirement, the thermal management system is used for customizing heat operation under performance loss, frostless control is started, the set value of the air supply quantity and the air supply temperature of the carriage is a fixed value, the set value gear can be selected automatically, the air supply quantity of the carriage is controlled by the rotating speed of the indoor fan 6, the air supply temperature of the carriage is controlled by the rotating speed of the compressor 1, the evaporation temperature is judged in real time, meanwhile, the opening of the all-pass throttle valve 4 is used for controlling the high-pressure value to approach the optimal exhaust pressure value in real time, and the target value T of the evaporation temperature is obtained eva0 The method is determined by the ambient temperature and humidity, and comprises the following specific steps:
the first step: the temperature and humidity values of the environment are measured by an outdoor thermometer 13 and an outdoor hygrometer 14, respectively denoted as T env And H env ；
And a second step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env )；
Third step, the evaporating temperature T of the refrigerant is collected eva Air supply temperature T of carriage sup Exhaust pressure value P dis ；
Fourth, control and regulation are started, the compressor 1 is started at the initial set rotation speed, and when T is the time eva >T dwe When-1, increasing the rotating speed of the compressor 1 to raise the air supply temperature, and simultaneously reducing the opening of the all-pass throttle valve 4 to enable the exhaust pressure value to approach the optimal exhaust pressure value, judging the evaporating temperature once every 10s, and when the evaporating temperature meets T eva <T dwe At the time of-1, the opening degree of the all-way throttle valve 4 starts to be increased until T eva ＝T dwe -1 and T sup ＝T sup-aim The pressure difference between the real-time exhaust pressure value and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation condition of the evaporator, so that the performance loss of the thermal management system is minimum;
(3) Control method of frostless control mode with high heating capacity requirement
Frostless control when the thermal management system is in high heating demandIn the mode, the heating requirement is large, the mass flow of the refrigerant is large, the pressure drop in the evaporator is large, the temperature of the outlet of the evaporator is lower than the evaporation temperature, the air supply quantity and the air supply temperature set value of the carriage are set as fixed values, the passengers automatically select the set value gear, the air supply quantity of the carriage is controlled by the rotating speed of the indoor fan 6, the air supply temperature of the carriage is controlled by the rotating speed of the compressor 1, the temperature of the refrigerant at the outlet of the evaporator is judged in real time, and meanwhile, the opening of the all-pass throttle valve 4 is used for controlling the high-pressure value to approach the optimal exhaust pressure value in real time, wherein the target value T of the temperature of the refrigerant at the outlet of the evaporator eva-out0 The method is determined by the ambient temperature and humidity, and comprises the following specific steps:
the first step: the temperature and humidity values of the environment are measured by an outdoor thermometer 13 and an outdoor hygrometer 14, respectively denoted as T env And H env ；
And a second step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env )；
Third step, collecting the refrigerant temperature T of the evaporator outlet of the refrigerant eva-out Air supply temperature T of carriage sup Exhaust pressure value P dis ；
Fourth, control and regulation are started, the compressor 1 is started at the initial set rotation speed, and when T is the time eva-out >T dwe When-1, increasing the rotating speed of the compressor 1 to raise the air supply temperature, and simultaneously reducing the opening of the all-pass throttle valve 4 to enable the exhaust pressure value to approach the optimal exhaust pressure value, judging the evaporating temperature once every 10s, and when the evaporating temperature meets T eva-out <T dwe At the time of-1, the opening degree of the all-way throttle valve 4 starts to be increased until T eva-out ＝T dwe -1 and T sup ＝T sup-aim The pressure difference between the real-time value of the exhaust pressure and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation condition of the evaporator, so that the performance loss of the thermal management system is minimum.
When the environmental working condition is in the frosting working condition, the vehicle thermal management system is started once, the heat is customized to run under the energy loss, and the control system starts a frostless control mode; during secondary start, in order to prevent the condensation phenomenon from occurring on the surface of the heat exchanger, the air humidity on the surface of the defrosting heat exchanger 3 is increased, therefore, a secondary start frostless control mode is adopted during secondary start, the air supply air quantity and the air supply temperature set value of the carriage are set values, the set value gear is selected independently, the air supply air quantity of the carriage is controlled by the rotating speed of the indoor fan 6, the air supply temperature of the carriage is controlled by the rotating speed of the compressor, and the specific determining steps are as follows:
the first step: the temperature of the environment is measured by an outdoor thermometer 13 and an outdoor hygrometer 14 and is denoted by T env ；
And a second step of: the maximum humidity corresponding to the temperature is H env-max ；
And a third step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env-max )；
Fourth, control and regulation are started, the compressor 1 is started at the initial set rotation speed, and when T is the time eva >T dwe When-1, increasing the rotating speed of the compressor 1 to raise the air supply temperature, and simultaneously reducing the opening of the all-pass throttle valve 4 to enable the exhaust pressure value to approach the optimal exhaust pressure value, judging the evaporating temperature once every 10s, and when the evaporating temperature meets T eva <T dwe At the time of-1, the opening degree of the all-way throttle valve 4 starts to be increased until T eva ＝T dwe -1 and T sup ＝T sup-aim The pressure difference between the real-time value of the exhaust pressure and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation condition of the evaporator, so that the performance loss of the thermal management system is minimum.
It will be appreciated by those skilled in the art that the present invention can be carried out in other embodiments without departing from the spirit or essential characteristics thereof. Accordingly, the above disclosed embodiments are illustrative in all respects, and not exclusive. All changes that come within the scope of the invention or equivalents thereto are intended to be embraced therein.
Claims (5)
1. The frostless control method of the new energy automobile thermal management system for transcritical carbon dioxide is characterized in that the new energy automobile thermal management system for transcritical carbon dioxide comprises the following steps: the device comprises a compressor (1), a first four-way reversing valve (2), a defrosting heat exchanger (3), a main heat exchanger (5), an indoor fan (6), a second four-way reversing valve (7), a heat regenerator (8), an outdoor heat exchanger (10) and a gas-liquid separator (11); the outlet of the compressor (1) is connected with the a port of the first four-way reversing valve (2), the b port of the first four-way reversing valve (2) is connected with the inlet of the defrosting heat exchanger (3), the outlet of the defrosting heat exchanger (3) is connected with the inlet of the main heat exchanger (5) through the all-way throttle valve (4), the a port of the second four-way reversing valve (7) is connected with the outlet of the main heat exchanger (5), the c port of the second four-way reversing valve (7) is connected with the d port of the regenerator (8) through the two-way throttle valve (9), the c port of the regenerator (8) is connected with the b port of the second four-way reversing valve (7), the d port of the second four-way reversing valve (7) is connected with the inlet of the outdoor heat exchanger (10), the outlet of the outdoor heat exchanger (10) is connected with the d port of the first four-way reversing valve (2), the c port of the first four-way reversing valve (2) is connected with the inlet of the gas-liquid separator (11), and the outlet of the gas-liquid separator (11) is connected with the inlet of the regenerator (8) a of the regenerator (1); the port a of the heat regenerator (8) is communicated with the port b of the heat regenerator (8); the c port of the heat regenerator (8) is communicated with the d port of the heat regenerator (8);
the frostless control method comprises the following steps: the method comprises the steps of collecting the ambient temperature and the relative humidity, and controlling the working mode of the transcritical carbon dioxide electric automobile thermal management system according to the ambient temperature and the relative humidity:
(1) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env not less than 5, or
T env <5，T dew ＝f(T env ,H env )，T env -T dew ≥N
Wherein T is dew N=5 for dew point temperature;
at the moment, the transcritical carbon dioxide electric automobile heat management system is controlled to operate in a conventional heating mode under the conventional heating working condition;
(2) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env <at 5, T dew ＝f(T env ,H env )，M<T env -T dew <N,
N＝5，M＝3.5；
At the moment, the trans-critical carbon dioxide electric automobile heat management system is controlled to operate in one of a conventional heating mode or a frostless control mode with low heating quantity requirement under the light frosting working condition;
(3) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
Q<T env <at 5, T dew ＝f(T env ,H env )，T env -T dew <M
Q＝-10；
At the moment, the trans-critical carbon dioxide electric automobile heat management system is controlled to operate in a frostless control mode with low heating quantity requirement under the severe frosting working condition with low heating quantity requirement;
(4) When the ambient temperature T env And relative humidity H env The method meets the following conditions:
T env when Q is less than or equal to Q, T dew ＝f(T env ,H env )，T env -T dew <M
At the moment, the trans-critical carbon dioxide electric automobile thermal management system is controlled to operate in a frostless control mode with high heating requirements under the severe frosting working condition with high heating requirements;
during the conventional heating mode, the ab channel of the first four-way reversing valve (2) is controlled to be communicated, the cd channel is controlled to be communicated, the ac channel of the second four-way reversing valve (7) is connected, the bd channel is connected, the regenerator (8) is in a small regenerative working mode, and the refrigerant after the two-way throttle valve (9) exchanges heat with the refrigerant at the outlet of the gas-liquid separator (11), so that the heat exchange amount is minimum;
or when the frostless control mode with low heating capacity is adopted, the ab channel of the first four-way reversing valve (2) is controlled to be communicated, the cd channel of the first four-way reversing valve is controlled to be communicated, the ab channel of the second four-way reversing valve (7) is connected, the cd channel of the second four-way reversing valve is connected, the regenerator (8) is in a large-regenerative working mode, the refrigerant at the outlet of the main heat exchanger (5) exchanges heat with the refrigerant at the outlet of the gas-liquid separator (11), and the heat exchange capacity is larger than that in the conventional heating mode;
or when the frostless control mode with high heating requirement is adopted, the ab channel of the first four-way reversing valve (2) is controlled to be communicated, the cd channel is controlled to be communicated, the ab channel of the second four-way reversing valve (7) is connected, the cd channel is connected, the regenerator (8) is in a large-regenerative working mode, the refrigerant at the outlet of the main heat exchanger (5) exchanges heat with the refrigerant at the outlet of the gas-liquid separator (11), and the heat exchange quantity is maximum;
or when the environmental working condition is in the frosting working condition, the thermal management system is started once, so that the heat can be customized to run under the loss, and the control system starts a frostless control mode; when the vehicle is started for the second time, a frostless control mode is started for the second time, the set value of the air supply quantity and the air supply temperature of the vehicle is a fixed value, the set value gear is selected automatically, the air supply quantity of the vehicle is controlled by the rotating speed of the indoor fan (6), the air supply temperature of the vehicle is controlled by the rotating speed of the compressor (1), and the specific determining steps are as follows:
the first step: the temperature of the environment is measured by an outdoor thermometer (13) and an outdoor hygrometer (14), and is marked as T env ；
And a second step of: the maximum humidity corresponding to the temperature is H env-max ；
And a third step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env-max )；
Fourth, control and regulation are started, the compressor (1) is started at an initial set rotation speed, and when T is the time eva >T dwe When in process of-1, the rotating speed of the compressor (1) is increased to raise the air supply temperature, and meanwhile, the opening of the all-pass throttle valve (4) is reduced to enable the exhaust pressure value to approach the optimal exhaust pressure value, the evaporating temperature is judged every 10s, and when the evaporating temperature meets T eva <T dwe At the time of-1, the opening degree of the all-pass throttle valve (4) starts to be increased until T eva ＝T dwe -1 and T sup ＝T sup-aim The pressure difference between the real-time value of the exhaust pressure and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation condition of the evaporator, so that the performance loss of the thermal management system is minimum.
2. The frostless control method according to claim 1, characterized in that when the thermal management system is in the normal heating mode, the air supply volume of the cabin is controlled by the rotational speed of the indoor fan (6), the air supply temperature of the cabin is controlled by the rotational speed of the compressor (1), and the optimum exhaust pressure value of the thermal management system is present to minimize the power consumption of the compressor (1) when customizing heat; the exhaust pressure of the thermal management system is controlled by the opening degree of a two-way throttle valve (9), the air quantity of an outdoor heat exchanger (10) is controlled by the rotating speed of an outdoor fan (12), wherein the optimal exhaust pressure P of the thermal management system under heating operation opt And ambient temperature T env Air inlet temperature T of carriage air And the air supply temperature T of the carriage sup Correlation: p (P) opt ＝f(T env ,T air ,T sup )。
3. The frostless control method according to claim 1, characterized in that when the thermal management system is in the frostless control mode with low heating capacity demand, the thermal management system is operated for customizing heat under performance loss, frostless control is started, the air supply volume of the carriage is controlled by the rotation speed of the indoor fan (6), the air supply temperature of the carriage is controlled by the rotation speed of the compressor (1), the evaporation temperature is judged in real time, and the opening degree of the all-pass throttle valve (4) is used for controlling the high pressure value to approach the optimal exhaust pressure value in real time, wherein the target value T of the evaporation temperature eva0 The method is determined by the ambient temperature and humidity, and comprises the following specific steps:
the first step: the temperature and humidity values of the environment are measured by an outdoor thermometer (13) and an outdoor hygrometer (14), respectively denoted as T env And H env ；
And a second step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env )；
Third step, the evaporating temperature T of the refrigerant is collected eva Air supply temperature T of carriage sup Exhaust pressure value P dis Target set value T of carriage air supply temperature set by passenger or manufacturer sup-aim ；
Fourth, control and regulation are started, the compressor (1) is started at the initial set rotation speed, and when T is the time eva >T dwe When in process of-1, the rotating speed of the compressor (1) is increased to raise the air supply temperature, and meanwhile, the opening of the all-pass throttle valve (4) is reduced to enable the exhaust pressure value to approach the optimal exhaust pressure value, the evaporating temperature is judged every 10s, and when the evaporating temperature meets T eva <T dwe At the time of-1, the opening degree of the all-pass throttle valve (4) starts to be increased until T eva ＝T dwe -1 and T sup ＝T sup-aim The pressure difference between the actual exhaust pressure value and the optimal exhaust pressure value is minimized on the premise of meeting the frostless operation of the outdoor heat exchanger (10), so that the performance loss of the thermal management system is minimized.
4. The frostless control method according to claim 1, characterized in that when the thermal management system is in the high heating demand frostless control mode, the air supply volume of the cabin is controlled by the rotational speed of the indoor fan (6), the air supply temperature of the cabin is controlled by the rotational speed of the compressor (1), the refrigerant temperature at the outlet of the evaporator is judged in real time, and the opening degree of the all-pass throttle valve (4) is used for controlling the high pressure value to approach the optimal exhaust pressure value in real time, wherein the target value T of the refrigerant temperature at the outlet of the evaporator eva-out0 The method is determined by the ambient temperature and humidity, and comprises the following specific steps:
the first step: the temperature and humidity values of the environment are measured by an outdoor thermometer (13) and an outdoor hygrometer (14), respectively denoted as T env And H env ；
And a second step of: inquiring a wet air physical property parameter table according to the collected environmental temperature and humidity value, and calculating the dew point temperature of the environmental air: t (T) dwe ＝f(T env ,H env )；
Third step, collecting the refrigerant temperature T of the evaporator outlet of the refrigerant eva-out Air supply temperature T of carriage sup Exhaust pressure value P dis ；
Fourth, control and regulation are started, the compressor (1) is started at an initial set rotation speed, and when T is the time eva-out >T dwe -1 increasing the rotational speed of the compressor (1)Raising the air supply temperature, simultaneously reducing the opening of the all-pass throttle valve (4) to enable the exhaust pressure value to approach the optimal exhaust pressure value, judging the evaporation temperature once every 10s, and when the evaporation temperature meets T eva-out <T dwe At the time of-1, the opening degree of the all-pass throttle valve (4) starts to be increased until T eva-out ＝T dwe -1 and T sup ＝T sup-aim At this time, the pressure difference between the real-time exhaust pressure value and the optimal exhaust pressure value is minimum on the premise of meeting the frostless operation of the outdoor heat exchanger, so that the performance loss of the thermal management system is minimum.
5. The frostless control method according to claim 1, characterized in that an outdoor fan (12) is provided beside the outdoor heat exchanger (10); an outdoor thermometer (13) and an outdoor hygrometer (14) are arranged at the outdoor heat exchanger (10).
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