CN111351246A - Non-azeotropic refrigerant self-overlapping heat pump air conditioning system - Google Patents
Non-azeotropic refrigerant self-overlapping heat pump air conditioning system Download PDFInfo
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- CN111351246A CN111351246A CN202010284831.1A CN202010284831A CN111351246A CN 111351246 A CN111351246 A CN 111351246A CN 202010284831 A CN202010284831 A CN 202010284831A CN 111351246 A CN111351246 A CN 111351246A
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 37
- 238000004378 air conditioning Methods 0.000 title claims abstract description 17
- 239000007788 liquid Substances 0.000 claims abstract description 46
- 238000001816 cooling Methods 0.000 claims abstract description 39
- 238000010438 heat treatment Methods 0.000 claims abstract description 34
- 238000004891 communication Methods 0.000 claims description 25
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 claims description 13
- 239000001294 propane Substances 0.000 claims description 7
- 239000000203 mixture Substances 0.000 claims description 6
- 239000007789 gas Substances 0.000 description 9
- 229910002092 carbon dioxide Inorganic materials 0.000 description 6
- 238000005057 refrigeration Methods 0.000 description 6
- 239000012530 fluid Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 3
- 239000007791 liquid phase Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000012071 phase Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000005431 greenhouse gas Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000005445 natural material Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a non-azeotropic refrigerant auto-cascade heat pump air conditioning system, which comprises an indoor heat exchanger, an outdoor heat exchanger, a gas-liquid separator, an internal heat exchanger, an evaporator, a liquid storage tank, a compressor, an air door, a first expansion valve, a second expansion valve and an evaporative condenser, wherein the indoor heat exchanger is connected with the outdoor heat exchanger through a pipeline; wherein the damper is adapted to be closed in the heating mode so that the cooling wind does not flow through the evaporator or to be opened in the cooling mode so that the cooling wind flows through the evaporator; the second expansion valve is adapted to be opened in the heating mode and closed in the cooling mode; a gas outlet of the gas-liquid separator is connected with a first inlet of the internal heat exchanger; the first outlet of the internal heat exchanger is connected to the first inlet of the evaporative condenser. The invention can realize high-efficiency operation in an ultra-wide temperature area by adopting self-cascade circulation, effectively solves the problem of serious attenuation of the performance efficiency of the heat pump at low temperature, improves the heating capacity, improves the comfort in the cabin by cold and hot switching, and meets the universality in cold and hot areas.
Description
Technical Field
The invention relates to a non-azeotropic refrigerant self-overlapping heat pump air conditioning system.
Background
Currently, 2016, 10, 15 days, under the Kyoli HFC amendment, all 197 countries in the United nations agree to gradually reduce the production and consumption of hydrofluorocarbons. Some developed countries start reducing HFC production and consumption from 2019 on a controlled basis, and others start 2020 a year after. In addition, two separate developing national communities react thereafter. The earlier of which would freeze HFC production and use in 2024, this community includes china and over 100 developing countries. Another smaller group, which includes only a few middle east countries as well as pakistan and india, will freeze the HFCs in 2028.
Conventional refrigerant R134a has a relatively high global warming potential (GWP 1430). The european union requires forced elimination of R134a on passenger cars and light commercial vehicles after 1 month 1 day 2017. The U.S. environmental protection agency and the national highway traffic safety administration have developed a national project for the purpose of reducing greenhouse gas emissions and improving fuel economy. More recently, the U.S. environmental protection agency has also listed R134a as a prohibited refrigerant for use in light automobiles that began to be newly produced in 2021.
The artificially synthesized refrigerant R1234yf was considered a suitable substitute for R134a because of its lower GWP value and thermodynamic properties close to those of R134 a. However, the limited supply and high price of R1234yf has led some original equipment manufacturers to research other solutions, R744 (CO) simultaneously2) Another option is offered by its low cost, non-flammability, high volumetric heat capacity, and perhaps most importantly by its environmental friendliness, i.e., it is a natural substance with an ODP of 0 and a GWP of 1.
However, CO2The biggest problem for the automobile air conditioner is that the performance is severely attenuated at high temperature, and the conventional CO is adopted at present2In the refrigeration cycle, the fluid at the inlet of the evaporator is directly from the throttled two-phase refrigerant, a certain amount of gas-phase refrigerant exists at the inlet of the evaporator, the dryness is high, and if the fluid entering the evaporator is liquid-phase refrigerant or the inlet dryness is low, the refrigeration performance is undoubtedly improved greatly.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a non-azeotropic refrigerant self-cascade heat pump air conditioning system, which can realize high-efficiency operation in an ultra-wide temperature area by adopting self-cascade circulation, effectively solve the problem of serious attenuation of the performance efficiency of a heat pump at low temperature, improve the heating capacity, improve the comfort in a cabin by cold-hot switching and meet the universality in cold and hot areas.
In order to solve the technical problems, the technical scheme of the invention is as follows: a non-azeotropic refrigerant auto-cascade heat pump air conditioning system comprises an indoor heat exchanger, an outdoor heat exchanger, a gas-liquid separator, an internal heat exchanger, an evaporator, a liquid storage tank, a compressor, an air door, a first expansion valve, a second expansion valve and an evaporative condenser; wherein,
the damper is adapted to be closed in the heating mode so that the cooling air does not flow through the evaporator or opened in the cooling mode so that the cooling air flows through the evaporator;
the second expansion valve is adapted to be opened in the heating mode and closed in the cooling mode;
a gas outlet of the gas-liquid separator is connected with a first inlet of the internal heat exchanger;
the first outlet of the internal heat exchanger is connected with the first inlet of the evaporative condenser;
a first outlet of the evaporative condenser is connected with a first expansion valve and then connected with an inlet of the evaporator;
the outlet of the evaporator is connected with the inlet of the liquid storage tank;
the outlet of the liquid storage tank is connected with the second inlet of the internal heat exchanger;
the second outlet of the internal heat exchanger is connected to the inlet of the compressor;
a liquid outlet of the gas-liquid separator is connected with a second expansion valve and then connected with a second inlet of the evaporative condenser, and a second outlet of the evaporative condenser is connected with the liquid storage tank;
in the heating mode, the outlet of the compressor is suitable for being connected with the inlet of the indoor heat exchanger, and the outlet of the indoor heat exchanger is suitable for being connected with the inlet of the gas-liquid separator;
in the refrigeration mode, the outlet of the compressor is suitable for being connected with the inlet of the outdoor heat exchanger, and the outlet of the outdoor heat exchanger is connected with the inlet of the gas-liquid separator.
The indoor bypass valve is connected between an inlet and an outlet of the indoor heat exchanger in parallel, and the indoor communication valve is connected to the inlet of the indoor heat exchanger;
the indoor communication valve is adapted to open in a heating mode and close in a cooling mode;
the indoor bypass valve is adapted to close in a heating mode and open in a cooling mode.
The outdoor heat exchanger further comprises an outdoor bypass valve and an outdoor communication valve, wherein the outdoor bypass valve is connected between an inlet and an outlet of the outdoor heat exchanger in parallel, and the outdoor communication valve is connected to the inlet of the outdoor heat exchanger;
the outdoor communication valve is adapted to be closed in a heating mode and open in a cooling mode;
the outdoor bypass valve is adapted to open in a heating mode and close in a cooling mode.
Furthermore, the outdoor heat exchanger is correspondingly provided with a cooling fan used for radiating heat of the outdoor heat exchanger.
Further, the air conditioner also comprises a fan which is suitable for providing cooling air for the indoor heat exchanger and/or the evaporator.
Further, the non-azeotropic refrigerant is natural refrigerant CO2And propane zeotropic mixtures.
After the technical scheme is adopted, CO is used2Propane non-azeotropic mixed refrigerant, which reduces the damage of traditional refrigerant to ozone layer and global warming problem, and makes up for the shortage of two refrigerants. In addition, the conventional automobile heat pump air-conditioning system is improved, and an air-conditioning structure for switching refrigeration and heating is provided; meanwhile, the performance is further improved by using the internal heat exchanger, and the energy consumption is reduced; in conclusion, the technical support is provided for the popularization and the application of the electric automobile in the global range.
Drawings
Fig. 1 is a schematic illustration of a non-azeotropic refrigerant self-cascade heat pump air conditioning system of the present invention in a heating mode;
FIG. 2 is a schematic illustration of a non-azeotropic refrigerant auto-cascade heat pump air conditioning system of the present invention in a cooling mode;
figure 3 is a pressure-enthalpy diagram of the cyclic process of the present invention.
Detailed Description
In order that the present invention may be more readily and clearly understood, a more particular description of the invention briefly described above will be rendered by reference to specific embodiments that are illustrated in the appended drawings.
As shown in fig. 1-2, a non-azeotropic refrigerant auto-cascade heat pump air conditioning system includes an indoor heat exchanger 2, an outdoor heat exchanger 7, a gas-liquid separator 10, an internal heat exchanger 6, an evaporator 4, a liquid storage tank 5, a compressor 13, a damper 3, a first expansion valve 14, a second expansion valve 11, and an evaporative condenser 12; wherein,
said damper 3 is adapted to be closed in the heating mode so that the cooling air does not flow through the evaporator 4 or to be opened in the cooling mode so that the cooling air flows through the evaporator 4;
the second expansion valve 11 is adapted to be opened in the heating mode and closed in the cooling mode;
the gas outlet of the gas-liquid separator 10 is connected to the first inlet of the internal heat exchanger 6;
a first outlet of the internal heat exchanger 6 is connected to a first inlet of the evaporative condenser 12;
a first outlet of the evaporative condenser 12 is connected with a first expansion valve 14 and then connected with an inlet of the evaporator 4;
the outlet of the evaporator 4 is connected with the inlet of the liquid storage tank 5;
the outlet of the liquid storage tank 5 is connected with the second inlet of the internal heat exchanger 6;
a second outlet of the internal heat exchanger 6 is connected to an inlet of the compressor 13;
a liquid outlet of the gas-liquid separator 10 is connected with a second expansion valve 11 and then connected with a second inlet of the evaporative condenser 12, and a second outlet of the evaporative condenser 12 is connected with the liquid storage tank 5;
in the heating mode, the outlet of the compressor 13 is adapted to be connected with the inlet of the indoor heat exchanger 2, and the outlet of the indoor heat exchanger 2 is adapted to be connected with the inlet of the gas-liquid separator 10;
in the cooling mode, the outlet of the compressor 13 is connected to the inlet of the outdoor heat exchanger 7, and the outlet of the outdoor heat exchanger 7 is connected to the inlet of the gas-liquid separator 10.
In the present embodiment, by using the internal heat exchanger 6, the high-pressure refrigerant and the low-pressure refrigerant exchange heat therebetween, on the one hand, the suction superheat is raised, and on the other hand, the high-temperature refrigerant flowing out of the outdoor heat exchanger 7 is further cooled.
In the embodiment, by using one evaporative condenser 12, the system can realize the cascade cycle only by using one compressor 13, and the temperature range of the system operation is widened.
By using the gas-liquid separator 10, separation of the gas-phase and liquid-phase refrigerants is achieved. In addition, the liquid storage tank 5 is used in the invention, so that the liquid-phase refrigerant is stored. The operation condition of the system is expanded, and the performance of the system is improved.
As shown in fig. 1-2, the heat exchanger further comprises an indoor bypass valve 16 and an indoor communication valve 15, wherein the indoor bypass valve 16 is connected in parallel between an inlet and an outlet of the indoor heat exchanger 2, and the indoor communication valve 15 is connected to the inlet of the indoor heat exchanger 2;
said indoor communication valve 15 is adapted to open in heating mode and to close in cooling mode;
the indoor bypass valve 16 is adapted to be closed in a heating mode and open in a cooling mode.
As shown in fig. 1-2, the heat exchanger further comprises an outdoor bypass valve 9 and an outdoor communication valve 8, wherein the outdoor bypass valve 9 is connected in parallel between an inlet and an outlet of the outdoor heat exchanger 7, and the outdoor communication valve 8 is connected to the inlet of the outdoor heat exchanger 7;
said outdoor communication valve 8 is adapted to be closed in heating mode and open in cooling mode;
the outdoor bypass valve 9 is adapted to be opened in the heating mode and closed in the cooling mode.
The first expansion valve 14 and the second expansion valve 11 may be electronic expansion valves.
The indoor communication valve 15, the indoor bypass valve 16, the outdoor communication valve 8, and the outdoor bypass valve 9 may be solenoid valves.
The embodiment also provides a refrigeration and heating switching mode for the system, specifically, 2 expansion valves, 4 electromagnetic valves and 1 air door 3 are arranged in the system, and the refrigeration and heating mode switching is realized through switching of different valves and switching of air doors. More specifically, in the cooling mode: the first expansion valve 14 operates as a throttle device, the second expansion valve 11 is closed, the outdoor communication valve 8, the indoor bypass valve 16 are opened, the outdoor bypass valve 9 and the indoor communication valve 15 are closed, the damper 3 is opened to allow air to flow through the evaporator 4, and the outdoor heat exchanger 7 functions as an air cooler; in the heating mode: the first expansion valve 14 and the second expansion valve 11 are operated, and the outdoor bypass valve 9 and the indoor communication valve 15 are opened, the outdoor communication valve 8 and the indoor bypass valve 16 are closed, and the damper 3 is closed to receive the evaporator 4.
As shown in fig. 1 to 2, the outdoor heat exchanger 7 is correspondingly provided with a cooling fan for dissipating heat from the outdoor heat exchanger 7.
As shown in fig. 1 to 2, the air conditioner further comprises a fan 1 adapted to supply cooling air to the indoor heat exchanger 2 and/or the evaporator 4.
Non-azeotropic refrigerants include, but are not limited to, the natural refrigerant CO2And propane zeotropic mixtures.
FIG. 1 is a diagram illustrating the operation of the present invention in a heating mode, CO2And propane as a non-azeotropic mixed refrigerant, which has excellent heating performance at low temperature, wherein the indoor communicating valve 15 is opened, the indoor bypass valve 16 is closed, high-pressure gas compressed by the compressor 13 is condensed into liquid through the indoor heat exchanger 2 for heating, and the air door 3 is closed. The outdoor bypass valve 9 is opened, the outdoor communication valve 8 is closed, and the outdoor heat exchanger 7 is bypassed and does not function. The fluid cooled by the indoor heat exchanger 2 is separated by a gas-liquid separator 10, the separated gas enters an evaporative condenser 12 through the hot end of the internal heat exchanger 6, is expanded by a first expansion valve 14 after being cooled, enters an evaporator 4 and then flows into a liquid storage tank 5; the liquid separated from the gas-liquid separator 10 is expanded by the second expansion valve 11 and flows into the evaporative condenser 12, where it is evaporated and flows into the liquid storage tank 5. The liquid in the liquid storage tank 5 passes through the internal heat exchanger 6 and then is circulated back and forth by the compressor 13.
Fig. 2 is a schematic illustration of the present invention operating in the cooling mode, with the indoor bypass valve 16 open, the indoor communication valve 15 closed, the gas compressed by the compressor 13, and the damper 3 open. The outdoor communication valve 8 is opened and the outdoor bypass valve 9 is closed. The high-temperature and high-pressure gas compressed by the compressor 13 passes through the indoor bypass valve 16, then passes through the outdoor communication valve 8, flows into the outdoor heat exchanger 7 to be cooled, and then flows into the gas-liquid separator 10, the second expansion valve 11 is closed, and the gas flows through the internal heat exchanger 6 and then enters the evaporative condenser 12. The first expansion valve 14 is opened, and the high-pressure fluid is expanded and flows into the evaporator 4. The evaporated gas flows into the liquid storage tank 5; the low-temperature gas in the liquid storage tank 5 flows into the compressor 13 through the internal heat exchanger 6 and is circulated to and fro.
To illustrate CO2Specific operation of the propane cycle system, the pressure-enthalpy diagram being shown in figure 3, the corresponding state points a-J being marked in figure 3. The entire cycle can be divided into three branches, each with its own composition, as shown in fig. 3, a low temperature stage E-F-G-H, labeled L, rich in the less volatile refrigerant carbon dioxide, and a high temperature stage D-I-J, labeled H, rich in the more highly volatile refrigerant propane. The lines for C-E, C-D and H-A, I-J represent the separation and mixing processes, respectively. B-C is the process of heating the carriage. If more CO is present in the mixture2Concentration, it can work as a transcritical cycle if less CO is present in the mixture2Concentration, then working as a subcritical cycle.
The above embodiments are described in further detail to solve the technical problems, technical solutions and advantages of the present invention, and it should be understood that the above embodiments are only examples of the present invention and are not intended to limit the present invention, and any modifications, equivalent substitutions, improvements and the like made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms indicating an orientation or positional relationship are based on the orientation or positional relationship shown in the drawings only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings or the orientations or positional relationships that the products of the present invention are conventionally placed in use, and are only used for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," and the like are used solely to distinguish one from another and are not to be construed as indicating or implying relative importance.
Furthermore, the terms "horizontal", "vertical", "overhang" and the like do not imply that the components are required to be absolutely horizontal or overhang, but may be slightly inclined. For example, "horizontal" merely means that the direction is more horizontal than "vertical" and does not mean that the structure must be perfectly horizontal, but may be slightly inclined.
In the present invention, unless otherwise expressly stated or limited, the first feature may be present on or under the second feature in direct contact with the first and second feature, or may be present in the first and second feature not in direct contact but in contact with another feature between them. Also, the first feature being above, on or above the second feature includes the first feature being directly above and obliquely above the second feature, or merely means that the first feature is at a higher level than the second feature. A first feature that underlies, and underlies a second feature includes a first feature that is directly under and obliquely under a second feature, or simply means that the first feature is at a lesser level than the second feature.
Claims (6)
1. A non-azeotropic refrigerant auto-cascade heat pump air conditioning system is characterized by comprising an indoor heat exchanger (2), an outdoor heat exchanger (7), a gas-liquid separator (10), an internal heat exchanger (6), an evaporator (4), a liquid storage tank (5), a compressor (13), an air door (3), a first expansion valve (14), a second expansion valve (11) and an evaporative condenser (12); wherein,
the damper (3) is adapted to be closed in a heating mode so that cooling air does not flow through the evaporator (4) or to be opened in a cooling mode so that cooling air flows through the evaporator (4);
the second expansion valve (11) is adapted to be opened in a heating mode and closed in a cooling mode;
the gas outlet of the gas-liquid separator (10) is connected with the first inlet of the internal heat exchanger (6);
the first outlet of the internal heat exchanger (6) is connected to the first inlet of the evaporative condenser (12);
a first outlet of the evaporative condenser (12) is connected with a first expansion valve (14) and then is connected with an inlet of the evaporator (4);
the outlet of the evaporator (4) is connected with the inlet of the liquid storage tank (5);
the outlet of the liquid storage tank (5) is connected with the second inlet of the internal heat exchanger (6);
the second outlet of the internal heat exchanger (6) is connected to the inlet of the compressor (13);
a liquid outlet of the gas-liquid separator (10) is connected with a second expansion valve (11) and then is connected with a second inlet of the evaporative condenser (12), and a second outlet of the evaporative condenser (12) is connected with the liquid storage tank (5);
in the heating mode, the outlet of the compressor (13) is suitable for being connected with the inlet of the indoor heat exchanger (2), and the outlet of the indoor heat exchanger (2) is suitable for being connected with the inlet of the gas-liquid separator (10);
in a cooling mode, the outlet of the compressor (13) is suitable for being connected with the inlet of the outdoor heat exchanger (7), and the outlet of the outdoor heat exchanger (7) is connected with the inlet of the gas-liquid separator (10).
2. The non-azeotropic refrigerant self-cascade heat pump air conditioning system according to claim 1,
the indoor heat exchanger is characterized by further comprising an indoor bypass valve (16) and an indoor communication valve (15), wherein the indoor bypass valve (16) is connected between an inlet and an outlet of the indoor heat exchanger (2) in parallel, and the indoor communication valve (15) is connected to the inlet of the indoor heat exchanger (2);
said indoor communication valve (15) being suitable for opening in heating mode and closing in cooling mode;
the indoor bypass valve (16) is adapted to be closed in a heating mode and open in a cooling mode.
3. The non-azeotropic refrigerant self-cascade heat pump air conditioning system according to claim 1,
the outdoor heat exchanger is characterized by further comprising an outdoor bypass valve (9) and an outdoor communicating valve (8), wherein the outdoor bypass valve (9) is connected between an inlet and an outlet of the outdoor heat exchanger (7) in parallel, and the outdoor communicating valve (8) is connected to the inlet of the outdoor heat exchanger (7);
said outdoor communication valve (8) being suitable for closing in heating mode and opening in cooling mode;
the outdoor bypass valve (9) is adapted to open in a heating mode and close in a cooling mode.
4. The non-azeotropic refrigerant self-cascade heat pump air conditioning system according to claim 1,
and the outdoor heat exchanger (7) is correspondingly provided with a cooling fan used for radiating heat of the outdoor heat exchanger (7).
5. The non-azeotropic refrigerant self-cascade heat pump air conditioning system according to claim 1,
the air conditioner also comprises a fan (1) which is suitable for providing cooling air for the indoor heat exchanger (2) and/or the evaporator (4).
6. The non-azeotropic refrigerant self-cascade heat pump air conditioning system according to claim 1,
the non-azeotropic refrigerant is natural refrigerant CO2And propane zeotropic mixtures.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010284831.1A CN111351246A (en) | 2020-04-13 | 2020-04-13 | Non-azeotropic refrigerant self-overlapping heat pump air conditioning system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010284831.1A CN111351246A (en) | 2020-04-13 | 2020-04-13 | Non-azeotropic refrigerant self-overlapping heat pump air conditioning system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113108503A (en) * | 2021-03-24 | 2021-07-13 | 中国科学院工程热物理研究所 | Heat pump set based on self-cascade circulation |
| CN114083960A (en) * | 2021-12-08 | 2022-02-25 | 珠海格力电器股份有限公司 | Automobile heat management air conditioning system and new energy automobile |
-
2020
- 2020-04-13 CN CN202010284831.1A patent/CN111351246A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113108503A (en) * | 2021-03-24 | 2021-07-13 | 中国科学院工程热物理研究所 | Heat pump set based on self-cascade circulation |
| CN114083960A (en) * | 2021-12-08 | 2022-02-25 | 珠海格力电器股份有限公司 | Automobile heat management air conditioning system and new energy automobile |
| CN114083960B (en) * | 2021-12-08 | 2023-06-30 | 珠海格力电器股份有限公司 | Automobile heat management air conditioning system and new energy automobile |
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