CN109747384B - Parallel compression type CO2 automobile heat pump air conditioning system with heat recovery device - Google Patents
Parallel compression type CO2 automobile heat pump air conditioning system with heat recovery device Download PDFInfo
- Publication number
- CN109747384B CN109747384B CN201910121025.XA CN201910121025A CN109747384B CN 109747384 B CN109747384 B CN 109747384B CN 201910121025 A CN201910121025 A CN 201910121025A CN 109747384 B CN109747384 B CN 109747384B
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- gas
- liquid separator
- air conditioning
- conditioning system
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000007906 compression Methods 0.000 title claims abstract description 22
- 230000006835 compression Effects 0.000 title claims abstract description 20
- 238000004378 air conditioning Methods 0.000 title claims abstract description 15
- 238000011084 recovery Methods 0.000 title claims description 10
- 239000007788 liquid Substances 0.000 claims abstract description 48
- 239000003507 refrigerant Substances 0.000 claims abstract description 23
- 238000005057 refrigeration Methods 0.000 claims abstract description 12
- 239000007791 liquid phase Substances 0.000 claims abstract description 6
- 230000000694 effects Effects 0.000 claims abstract description 3
- 238000005457 optimization Methods 0.000 claims abstract 2
- 239000012530 fluid Substances 0.000 claims description 24
- 238000010438 heat treatment Methods 0.000 claims description 18
- 238000001816 cooling Methods 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 10
- 239000012071 phase Substances 0.000 claims description 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 239000007789 gas Substances 0.000 abstract description 25
- 230000008878 coupling Effects 0.000 abstract description 2
- 238000010168 coupling process Methods 0.000 abstract description 2
- 238000005859 coupling reaction Methods 0.000 abstract description 2
- 238000005265 energy consumption Methods 0.000 abstract description 2
- 230000029058 respiratory gaseous exchange Effects 0.000 abstract description 2
- 239000007792 gaseous phase Substances 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000001172 regenerating effect Effects 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Images
Landscapes
- Air-Conditioning For Vehicles (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Parallel compression with heat regeneratorFormula CO2Automotive heat pump air conditioning system, comprising: two parallel scroll compressors, gas cooler, outdoor heat exchanger, middle heat exchanger, vapour and liquid separator, evaporimeter and the liquid storage pot of coaxial coupling, wherein: the output of two scroll compressors is in proper order with gas cooler, outdoor heat exchanger, middle heat exchanger links to each other with vapour and liquid separator, vapour and liquid separator's gaseous phase output end links to each other with second scroll compressor's input, vapour and liquid separator's liquid phase output links to each other with evaporimeter and liquid storage pot in proper order and links to each other with first scroll compressor's input through middle heat exchanger, and middle heat exchanger promotes the high temperature refrigerant that further cools off gas cooler outflow when breathing in the superheat degree, and the performance optimization is realized with the superposition of parallel compression effect. In the refrigeration mode, the parallel compression scheme is adopted, and CO is solved2The efficiency of the refrigerant is reduced in a high-temperature environment, and the energy consumption is reduced.
Description
Technical Field
The invention relates to the technology in the field of vehicle air conditioners, in particular to a parallel compression type CO with a heat regenerative device2Automobile heat pump air conditioning system.
Background
For heating in winter, compared with the traditional internal combustion engine automobile, the electric automobile has no available engine waste heat, and the heat pump technology is increasingly popularized on the electric automobile. The refrigerant commonly used by the current automobile air conditioner is R134a, but the refrigerant has very high GWP (global warming potential) and very poor heating performance at low temperature, and the search for a proper substitute refrigerant and the heat pump technology are particularly important.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides a parallel compression type CO with a heat regenerative device2The automobile heat pump air conditioning system can be switched between the refrigeration mode and the heating mode without being influenced by the ambient temperature and the type of the vehicle.
The heat pump system can use a natural refrigerant R744, reduce the influence on the environment and solve the problem of heating requirement at low temperature, and is realized by the following technical scheme:
the invention comprises the following steps: two parallel scroll compressors, gas cooler, outdoor heat exchanger, middle heat exchanger, vapour and liquid separator, evaporimeter and the liquid storage pot of coaxial coupling, wherein: the output of first scroll compressor and second scroll compressor links to each other with gas cooler's input, gas cooler's output passes through outdoor heat exchanger and links to each other with the high pressure input of middle heat exchanger, the high pressure output of middle heat exchanger links to each other with vapour and liquid separator's input, vapour and liquid separator's gas output end links to each other with second scroll compressor's input, vapour and liquid separator's liquid output end links to each other with evaporimeter and liquid storage pot in proper order, the output of liquid storage pot links to each other with middle heat exchanger's low pressure input, middle heat exchanger's low pressure output links to each other with first scroll compressor's input, when middle heat exchanger promotes the degree of superheat of breathing in further cools off the high temperature refrigerant that gas cooler flows, realize the performance.
First to third electronic expansion valves and first to third electromagnetic valves are respectively and correspondingly arranged between the evaporator and the gas-liquid separator, between the gas-liquid separator and the intermediate heat exchanger, and between the gas cooler and the outdoor heat exchanger.
The invention relates to a refrigerating and heating switching method of the air conditioning system, which realizes the switching between a refrigerating mode and a heating mode by switching an electronic expansion valve and an electromagnetic valve, changing and using a heat exchanger and switching an air door.
The refrigeration mode is as follows: the first electronic expansion valve and the second electronic expansion valve operate and enable the fluid to be expanded twice, the third electronic expansion valve is closed, the first electromagnetic valve and the third electromagnetic valve are opened, the second electromagnetic valve is closed, the air door is closed to prevent the gas cooler from participating in heat exchange, and the outdoor heat exchanger serves as the gas cooler at the moment.
The heating mode is as follows: the third electronic expansion valve operates, the other electronic expansion valves are closed, the second electromagnetic valve is opened, the other electromagnetic valves are closed, the air door is opened to enable air to flow through the gas cooler, the outdoor heat exchanger serves as an evaporator at the moment, the gas-liquid separator serves as a liquid storage tank to store liquid-phase refrigerant, the evaporator and the liquid storage tank in the original refrigeration mode, the intermediate heat exchanger and the first scroll compressor do not work, and no fluid participates in circulation.
Technical effects
Compared with the prior art, the invention uses natural environment-friendly refrigerant CO2The damage of the traditional refrigerant to the ozone layer and the global warming problem are reduced. The invention is characterized in that novel CO is designed2The heat pump air conditioning system also discloses the simple switching operation of the cooling and heating modes. In a refrigeration mode, a parallel compression scheme is adopted, and CO is solved2The efficiency of the refrigerant is attenuated in a high-temperature environment, the performance of the refrigeration system is further improved by using the intermediate heat exchanger, the energy consumption is reduced, and experimental data show that the refrigeration efficiency is improved by 15-20% compared with a conventional refrigeration system. The system can efficiently operate at the temperature of minus 20 ℃ to 40 ℃, and the temperature range covers most regions of China, so that the application of the system is not limited by the territory.
Drawings
FIG. 1 is a schematic view of the present invention in a cooling mode;
FIG. 2 is a pressure enthalpy diagram of the present invention in a cooling mode;
FIG. 3 is a schematic view of the present invention in a heating mode;
in the figure: the heat exchanger comprises a heat exchanger fan 1, a centrifugal fan 2, an evaporator 3, a damper 4 in a heating mode, a damper 5 in a cooling mode, a gas cooler 6, a wind direction 7, a first electronic expansion valve 8, a first electromagnetic valve 9, a liquid storage tank 10, an intermediate heat exchanger 11, a second electromagnetic valve 12, a second electronic expansion valve 13, a low-pressure input end 14, a low-pressure output end 15, a high-pressure input end 16, a high-pressure output end 17, a gas-liquid separator 18, a first scroll compressor 19, a first scroll compressor outlet 20, a first scroll compressor inlet 21, a second scroll compressor outlet 22, a second scroll compressor inlet 23, a second scroll compressor 24, a third electronic expansion valve 25, a third electromagnetic valve 26 and an outdoor heat exchanger 27.
Detailed Description
As shown in fig. 1, the present embodiment includes: two parallel scroll compressors 19 and 24, a gas cooler 6, an outdoor heat exchanger 27, an intermediate heat exchanger 11, a gas-liquid separator 18, an evaporator 3 and a liquid storage tank 10, which are coaxially connected, wherein: the first vortex compressor outlet 20 and the second vortex compressor outlet 22 are connected with the input end of the gas cooler 6, the output end of the gas cooler 6 is connected with the high-pressure input end 16 of the intermediate heat exchanger 11 through the outdoor heat exchanger 27, the high-pressure output end 17 of the intermediate heat exchanger 11 is connected with the input end of the gas-liquid separator 18, the gas output end of the gas-liquid separator 18 is connected with the second vortex compressor inlet 23, the liquid output end of the gas-liquid separator 18 is sequentially connected with the evaporator 3 and the liquid storage tank 10, the output end of the liquid storage tank 10 is connected with the low-pressure input end 14 of the intermediate heat exchanger 11, the low-pressure output end 15 of the intermediate heat exchanger 11 is connected with the first vortex compressor inlet 21, on one hand, the intermediate heat exchanger 11 improves the suction superheat degree, on the other hand, the, thereby improving system performance.
First to third electronic expansion valves 8, 13 and 25 and first to third electromagnetic valves 9, 12 and 26 are respectively and correspondingly arranged between the evaporator 3 and the gas-liquid separator 18, between the gas-liquid separator 18 and the intermediate heat exchanger 11 and between the gas cooler 6 and the outdoor heat exchanger 27.
The outdoor heat exchanger 27 is provided with a fan 1.
Upstream of the evaporator 3 and the gas cooler 6 a centrifugal fan 2 is arranged, the wind direction 7 of which centrifugal fan 2 is shown in fig. 1 and 3.
The air conditioning box is provided with two air doors 4 and 5.
This example is in refrigeration mode, CO2The refrigerant is evaporated in the evaporator 3 and enters the liquid storage tank 10, the fluid enters the high-pressure fluid from the low-pressure input end 14 of the intermediate heat exchanger 11 for heat exchange and then flows out from the low-pressure output end 15 of the intermediate heat exchanger 11, then enters the first scroll compressor 19 from the first scroll compressor inlet 21, flows out from the first scroll compressor outlet 20 after being compressed, and then passes through the gas cooler 6, because the gas cooler 6 at the moment is blocked by the air door 5 in the refrigeration mode and does not participate in the heat exchange, the fluid only flows through the third electromagnetic valve 26, flows into the outdoor heat exchanger 27 and is radiated by the fan 1, the fluid flowing out of the outdoor heat exchanger 27 flows in from the high-pressure input end 16 of the intermediate heat exchanger 11 and flows out from the high-pressure output end 17 of the intermediate heat exchanger 11 after exchanging heat with the low-pressure fluid, then the fluid is subjected to the first throttling by the second electronic expansion valve 13, and the, the separated gas-phase refrigerant enters a second scroll compressor 24 which runs in parallel with the first scroll compressor 19 from a second scroll compressor inlet 23, the gas-phase refrigerant flows out from a second scroll compressor outlet 22 after being compressed and is merged with the fluid flowing out of the first scroll compressor 19, the separated liquid-phase refrigerant flows through a first electromagnetic valve 9 and is throttled for the second time by a first electronic expansion valve 8, the throttled fluid returns to the evaporator 3 for evaporation, and therefore, CO2The vehicle refrigeration cycle is completed.
Referring to FIG. 2, which is a pressure-enthalpy diagram of the system in the cooling mode shown in FIG. 1, A-B-C-K-A in the diagram represents a conventional vapor compression cycle without a recuperator, A-B-C-D-E-F-A (D-G-H-C) represents a parallel compression cycle without a recuperator, and A-O-P-C-M-N-E-F-A (N-G-H-M) represents a parallel compression cycle with a recuperator according to the present invention. Wherein A-O denotes the fluid in the intermediate heat exchanger 11The heat exchange process at the low pressure side, O-P represents the compression process of the fluid in the first scroll compressor 19, G-H represents the compression process of the fluid in the second scroll compressor 24, P-C-M represents the heat exchange process of the fluid in the outdoor heat exchanger 27 and the further cooling process in the low pressure side of the intermediate heat exchanger 14, M-N represents the first throttling process of the fluid second in the electronic expansion valve 13, E-F represents the second throttling process of the fluid in the first electronic expansion valve 8, and finally, F-a represents the evaporation process of the fluid in the evaporator 3. Refrigerating capacity Q of parallel compression cycle system without heat recovery deviceeBy the formula: qe＝(1-xD)(hA-hF) Computing power consumption WcBy the formula: wc＝xD(hH-hG)+(1-xD)(hB-hA) Calculating, wherein: x is the number ofDIs the dryness of point D and the calculation formula is
h is the enthalpy value corresponding to each point. Thereby obtaining energy efficiency
Compared with the traditional vapor compression cycle A-B-C-K, the performance is greatly improved. In addition, in the parallel compression system with the heat recovery device, the high-temperature refrigerant from the gas cooler is subjected to heat exchange with the low-temperature refrigerant and then is throttled, so that the dryness of a point D is reduced, and as shown by a dotted line in fig. 2, the system performance is further improved.
As shown in fig. 3, in the heating mode, the outdoor heat exchanger 27 is used as an evaporator, the refrigerant absorbs heat and evaporates, and the gas-liquid separator 18 is used as a liquid storage tank for storing liquid-phase refrigerant, CO2After the refrigerant is evaporated in the evaporator at this time, the refrigerant enters the intermediate heat exchanger 11 and then flows into the liquid storage tank at this time through the second electromagnetic valve 12, the second electronic expansion valve 13 and the first electromagnetic valve are both closed, so that the fluid cannot flow through, the fluid flowing out of the liquid storage tank flows through the second scroll compressor 24 to be compressed, the first scroll compressor 19 at this time is closed, and the fluid flows out of the second scroll compressor 24 and then enters the gas for coolingThe air door 4 is opened in the heating mode, air flows through the gas cooler 6 to be heated and then is used for heating the automobile cabin, fluid from the gas cooler 6 enters the throttling mode through the third electronic expansion valve 25, the throttled fluid returns to the evaporator at the moment to be evaporated, and therefore CO is obtained2The vehicle heating cycle is completed.
The foregoing embodiments may be modified in many different ways by those skilled in the art without departing from the spirit and scope of the invention, which is defined by the appended claims and all changes that come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.
Claims (9)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910121025.XA CN109747384B (en) | 2019-02-19 | 2019-02-19 | Parallel compression type CO2 automobile heat pump air conditioning system with heat recovery device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910121025.XA CN109747384B (en) | 2019-02-19 | 2019-02-19 | Parallel compression type CO2 automobile heat pump air conditioning system with heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109747384A CN109747384A (en) | 2019-05-14 |
| CN109747384B true CN109747384B (en) | 2021-06-11 |
Family
ID=66407491
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910121025.XA Active CN109747384B (en) | 2019-02-19 | 2019-02-19 | Parallel compression type CO2 automobile heat pump air conditioning system with heat recovery device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109747384B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114312237A (en) * | 2020-09-30 | 2022-04-12 | 威马智慧出行科技（上海）有限公司 | Thermal management system of electric vehicle |
| CN112728799B (en) * | 2020-12-09 | 2021-12-10 | 上海交通大学 | Flash Evaporation System Based on CO2 Mixed Refrigerant |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6205802B1 (en) * | 2000-01-05 | 2001-03-27 | Carrier Corporation | Travel coach air conditioning system |
| CN105190197A (en) * | 2013-05-02 | 2015-12-23 | 艾默生环境优化技术有限公司 | Climate-control system having multiple compressors |
| US9358856B2 (en) * | 2013-10-03 | 2016-06-07 | Ford Global Technologies, Llc | System off configuration for climate control system |
| CN106352577A (en) * | 2016-08-26 | 2017-01-25 | 珠海格力电器股份有限公司 | Heat pump system, vehicle-mounted air conditioner and control method |
| CN106440441A (en) * | 2016-09-28 | 2017-02-22 | 西安交通大学 | A transcritical CO2 composite heat pump and its control method |
| CN206171115U (en) * | 2016-10-17 | 2017-05-17 | 重庆超力高科技股份有限公司 | CO2 heat pump air conditioning system |
| CN106671740A (en) * | 2017-01-03 | 2017-05-17 | 埃贝思(天津）新能源技术有限公司 | Energy-saving type vehicle-mounted refrigerating system |
| CN107843020A (en) * | 2017-12-08 | 2018-03-27 | 天津商业大学 | A kind of Trans-critical cycle CO2Two-stage Compression is pressurized refrigeration system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7600390B2 (en) * | 2004-10-21 | 2009-10-13 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
-
2019
- 2019-02-19 CN CN201910121025.XA patent/CN109747384B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6205802B1 (en) * | 2000-01-05 | 2001-03-27 | Carrier Corporation | Travel coach air conditioning system |
| CN105190197A (en) * | 2013-05-02 | 2015-12-23 | 艾默生环境优化技术有限公司 | Climate-control system having multiple compressors |
| US9358856B2 (en) * | 2013-10-03 | 2016-06-07 | Ford Global Technologies, Llc | System off configuration for climate control system |
| CN106352577A (en) * | 2016-08-26 | 2017-01-25 | 珠海格力电器股份有限公司 | Heat pump system, vehicle-mounted air conditioner and control method |
| CN106440441A (en) * | 2016-09-28 | 2017-02-22 | 西安交通大学 | A transcritical CO2 composite heat pump and its control method |
| CN206171115U (en) * | 2016-10-17 | 2017-05-17 | 重庆超力高科技股份有限公司 | CO2 heat pump air conditioning system |
| CN106671740A (en) * | 2017-01-03 | 2017-05-17 | 埃贝思(天津）新能源技术有限公司 | Energy-saving type vehicle-mounted refrigerating system |
| CN107843020A (en) * | 2017-12-08 | 2018-03-27 | 天津商业大学 | A kind of Trans-critical cycle CO2Two-stage Compression is pressurized refrigeration system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109747384A (en) | 2019-05-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107323217B (en) | Waste heat driven absorption refrigeration auxiliary supercooling CO 2 Automobile air conditioner | |
| CN111619311A (en) | CO (carbon monoxide)2Heat pump air conditioner whole vehicle heat management system | |
| JP6554156B2 (en) | Multistage heat pump having a two-stage expansion structure using CO2 refrigerant and its circulation method | |
| CN106414127A (en) | Automotive air conditioning system | |
| CN111351246B (en) | Non-azeotropic refrigerant self-cascade heat pump air conditioning system | |
| CN110171267A (en) | Electric automobile heat-pump air-conditioning system | |
| JP2002156161A (en) | Air conditioner | |
| CN105650921A (en) | Dual-stage compression refrigeration circulating system for cooling flashing gas bypass in stepped mode | |
| CN109747384B (en) | Parallel compression type CO2 automobile heat pump air conditioning system with heat recovery device | |
| CN208170776U (en) | A kind of gas compensating type electric automobile heat-pump air-conditioning system | |
| CN108638785B (en) | Novel electric automobile heat pump air conditioning system based on phase change energy storage defrosting and control method thereof | |
| CN110497769B (en) | Automobile heat pump system and control method thereof | |
| CN105352213A (en) | Steam and air cascade refrigerating system | |
| CN213984106U (en) | Carbon dioxide refrigeration air-conditioning system | |
| CN205561326U (en) | Dodge gas bypass step refrigerated doublestage compression freezing cycle system | |
| CN113701381A (en) | Transcritical carbon dioxide heat pump air conditioning system with low-pressure bypass valve | |
| CN112524832A (en) | Novel air-conditioning refrigeration system adopting carbon dioxide for refrigeration | |
| CN108692520B (en) | Internal overlapping refrigerator system using air supply compressor and control method | |
| CN206953941U (en) | A kind of CO2 air conditioning for automobiles of waste heat driving absorption refrigeration auxiliary supercooling | |
| CN206637882U (en) | Switchable type double evaporators CO2 trans critical cycle refrigeration systems | |
| CN119137421A (en) | Outdoor unit and multi-function water source multi-split system | |
| CN206426804U (en) | A kind of CO 2 cross-critical kind of refrigeration cycle automotive air-conditioning system | |
| CN212157715U (en) | A supercooled transcritical CO2 system with ejector booster cascade | |
| CN211823242U (en) | Non-azeotropic refrigerant self-overlapping heat pump air conditioning system | |
| CN211000833U (en) | Automotive heat pump system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |