CN112556230A - Ship solar vapor compression refrigeration cycle system with two-stage ejector - Google Patents
Ship solar vapor compression refrigeration cycle system with two-stage ejector Download PDFInfo
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- CN112556230A CN112556230A CN202110012442.8A CN202110012442A CN112556230A CN 112556230 A CN112556230 A CN 112556230A CN 202110012442 A CN202110012442 A CN 202110012442A CN 112556230 A CN112556230 A CN 112556230A
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63J—AUXILIARIES ON VESSELS
- B63J2/00—Arrangements of ventilation, heating, cooling, or air-conditioning
- B63J2/12—Heating; Cooling
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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
- F25B27/00—Machines, plants or systems, using particular sources of energy
- F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
- F25B27/005—Machines, plants or systems, using particular sources of energy using solar energy in compression type systems
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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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Ocean & Marine Engineering (AREA)
- Jet Pumps And Other Pumps (AREA)
Abstract
本发明的目的是提供一种带双级喷射器的船舶太阳能蒸气压缩制冷循环系统，制冷循环中太阳能喷射制冷机组充分利用海上太阳能完成制冷剂的低压级压缩，减少船舶对化石能源的依赖；双级喷射器结构简单、投入成本低、不易损坏、运行稳定，利用双级喷射器降低节流过程的不可逆损失，有效降低压缩机功耗，与普通蒸气压缩循环相比，该系统系统运作效率高，能耗低。
The purpose of the present invention is to provide a marine solar vapor compression refrigeration cycle system with a dual-stage ejector. In the refrigeration cycle, the solar energy injection refrigeration unit makes full use of the marine solar energy to complete the low-pressure stage compression of the refrigerant, thereby reducing the dependence of the ship on fossil energy; The single-stage ejector has simple structure, low investment cost, is not easy to be damaged, and operates stably. The double-stage ejector is used to reduce the irreversible loss of the throttling process and effectively reduce the power consumption of the compressor. Compared with the ordinary vapor compression cycle, the system has high operating efficiency. ,Low energy consumption.
Description
Technical Field
The invention relates to a refrigeration cycle system, in particular to a solar vapor compression refrigeration cycle system with a double-stage ejector for a ship.
Background
With the rapid development of the global shipping industry and the increasing importance of the environment protection in the world, the country puts higher demands on ship power equipment. The current technical level of ship equipment is still in the stage of inefficiency, and according to statistics, the emission of ship diesel engines causes about 5% -10% of atmospheric pollution in the global range. In the face of the current situation of energy shortage and increasingly severe environmental problems, how to reduce the emission of ship power equipment is a problem that needs to be continuously improved in the field of ships. Therefore, analyzing and improving the problems of refrigeration units, and fully utilizing renewable resources is a reliable way to reduce the energy efficiency of existing refrigeration units.
Offshore solar energy resources are very abundant, and solar ships have become a research trend, wherein solar jet refrigeration is an effective way for fully utilizing the solar energy resources. The ejector is used as a throttling device for recovering expansion pressure, has the advantages of no need of maintenance, simple structure, low cost and the like, but the traditional single-stage ejector has poor pressure boosting capacity and low efficiency, can not well realize low-temperature refrigeration, and the possibility of improving the system operation efficiency by adopting an adjustable two-stage ejector is realized.
Disclosure of Invention
The invention aims to provide a refrigeration cycle system, in particular to a ship solar vapor compression refrigeration cycle system with a two-stage ejector.
The invention adopts the technical scheme that the ship solar vapor compression refrigeration cycle system with the two-stage ejector comprises a high-pressure-stage vapor compression injection cycle system, a low-pressure-stage injection cycle system and a solar heat collection cycle system which are sequentially connected.
In the scheme, the method comprises the following steps: the high-pressure stage vapor compression injection cycle is a closed loop formed by a high-pressure stage compressor, a condenser, a high-pressure two-stage ejector and an intercooler which are sequentially connected, an outlet pipeline of the condenser is connected with a main flow inlet pipeline of the high-pressure two-stage ejector, an outlet pipeline of the high-pressure two-stage ejector is connected with an inlet pipeline of the intercooler, a refrigerant gas outlet pipeline of the intercooler is connected with an inlet pipeline of the high-pressure stage compressor and a secondary flow inlet pipeline of the high-pressure two-stage ejector and is connected with the low-pressure stage injection cycle through the intercooler, one part of gaseous refrigerant in the intercooler enters the high-pressure stage compressor, the other part of gaseous refrigerant enters the high-pressure two.
The low-pressure stage injection circulation is a closed loop formed by a generator, an intercooler, a low-pressure two-stage injector, an evaporator, a gas-liquid separator, an electronic expansion valve, an electromagnetic three-way valve, a low-pressure stage compressor and a circulating pump which are connected in sequence, the liquid outlet pipeline of the intercooler is connected with a main flow inlet pipeline of the low-pressure two-stage ejector, the outlet pipeline of the low-pressure two-stage ejector is connected with an inlet pipeline of a gas-liquid separator, a gas outlet of the gas-liquid separator is respectively connected with an inlet pipeline of a low-pressure stage compressor and an inlet pipeline of a generator refrigerant through an electromagnetic three-way valve, the outlet pipeline of the generator is connected with an inlet pipeline of a circulating pump, the outlet pipeline of the low-pressure stage compressor and the outlet pipeline of the circulating pump are connected with the inlet pipeline of the intercooler through the electromagnetic three-way valve, the liquid refrigerant outlet pipeline of the gas-liquid separator is connected with an inlet pipeline.
The solar heat collection circulation comprises a solar heat collector, a generator and a circulating pump which are sequentially connected to form a closed loop, an outlet pipeline of the solar heat collector is connected with a heat medium inlet pipeline of the generator, a heat medium outlet pipeline of the generator is connected with an inlet pipeline of the circulating pump, an outlet pipeline of the circulating pump is connected with an inlet pipeline of the solar heat collector, the solar heat collector and the low-pressure stage jet circulation share the generator, heat is released by the heat medium in the generator, and a refrigerant absorbs heat in the generator to become superheated steam.
Compared with the common two-stage vapor compression circulation system, the ship solar vapor compression refrigeration circulation system with the two-stage ejector provided by the invention has the advantages that solar energy of renewable energy sources is charged and utilized, and solar heat collection circulation can replace a low-pressure stage compressor to carry out one-stage boosting on a refrigerant; when the illumination condition can not meet the working requirement of the solar heat collection circulating unit, the system starts the low-pressure stage compressor to perform first-stage compression of the refrigerant.
The adjustable double-stage ejector provided by the invention can distribute the flow of the refrigerant entering the first-stage ejector and the second-stage ejector through a control algorithm, and can realize better adjusting and boosting capacity compared with a single-stage ejector.
The safety measures adopted by the invention are as follows:
the high-pressure double-stage ejector is connected with an intercooler pipeline and is provided with a check valve, so that the refrigerant is prevented from flowing back to the high-pressure double-stage ejector; the low-pressure double-stage ejector is connected with a gas-liquid separator pipeline and is provided with a check valve, so that the refrigerant is prevented from flowing back to the low-pressure double-stage ejector; the low pressure stage compressor is connected with the intercooler pipeline and is provided with a check valve, so that the refrigerant is prevented from flowing back to the low pressure stage compressor.
The advantages of the present invention are as follows.
1. In the refrigeration system, under the condition of sufficient illumination conditions, the solar heat collection cycle is used for replacing a low-pressure stage compressor to perform primary compression on the refrigerant; under the condition of insufficient illumination conditions, the working mode of the low-pressure compressor can be switched to, and intelligent energy conservation is realized.
2. The refrigerating system provided by the invention provides the adjustable secondary ejector, so that better pressure boosting capacity and adjusting capacity can be realized, the irreversible loss is reduced, and the refrigerating capacity of the system is improved.
3. According to the refrigeration system, low-temperature and low-pressure refrigerant from the evaporator in the low-pressure stage injection cycle is boosted in advance through the low-pressure two-stage ejector, so that the boosting capacity of the low-pressure injection cycle is improved.
4. According to the refrigeration system, the high-pressure two-stage ejector is used for throttling and recovering the expansion pressure in the high-pressure stage vapor compression injection circulation, so that the throttling loss can be reduced.
5. According to the refrigeration system, the condenser adopts a seawater cooling mode, so that the equipment operation cost is reduced, and the system operation efficiency is improved.
Drawings
FIG. 1 is a schematic view of a solar vapor compression refrigeration cycle system for a marine vessel with a dual stage ejector according to the present invention; the names of the main components in fig. 1 are: 1-a high pressure stage compressor; 2-a condenser; 3-a high pressure two stage ejector; 4-an intercooler; 5-low pressure dual stage ejector; 6-an evaporator; 7-gas-liquid separator; 8-low pressure stage compressor; 9-a generator; 10 a-a circulation pump; 10 b-a circulation pump; 11-a heat collector; 12-high pressure stage vapor compression injection cycle unit; 13-low pressure stage jet cycle machine set; 14-solar heat collection circulating unit; e-an electronic expansion valve; a C-check valve; f-electromagnetic three-way valve.
FIG. 2 is a schematic diagram of a two-dimensional configuration of a dual stage ejector according to the present invention; the names of the components in fig. 2 are: 15-a valve plate; 16-a primary working fluid inlet; 17-an ejection fluid inlet; 18-a primary receiving chamber; 19-a primary nozzle; 20-a primary mixing chamber; 21-a primary pressure-expanding chamber; 22-a secondary working fluid inlet; 23-a secondary nozzle; 24-a secondary receiving chamber; 25-a secondary mixing chamber; 26-secondary diffusion chamber.
Detailed Description
The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.
The ship solar vapor compression refrigeration cycle system with the two-stage ejector in the embodiment includes, as shown in fig. 1, a high-pressure stage vapor compression injection cycle unit 12, a low-pressure stage injection cycle unit 13, and a solar heat collection cycle unit 14, and specifically includes a high-pressure stage compressor 1, a condenser 2, a high-pressure two-stage ejector 3, an intercooler 4, a low-pressure two-stage ejector 5, an evaporator 6, a gas-liquid separator 7, a low-pressure stage compressor 8, a generator 9, a circulation pump 10a, a circulation pump 10b, a heat collector 11, an electronic expansion valve E, a check valve C, and an electromagnetic three-way valve F.
The high-pressure stage vapor compression injection circulation unit 12 is a closed loop formed by a high-pressure stage compressor 1, a condenser 2, a high-pressure two-stage injector 3 and an intercooler 4; an outlet pipeline of the condenser 2 is connected with a main flow inlet pipeline of a high-pressure two-stage ejector 3, an outlet pipeline of the high-pressure two-stage ejector 3 is connected with an inlet pipeline of an intercooler 4, a refrigerant gas outlet pipeline of the intercooler 4 is connected with an inlet pipeline of the high-pressure stage compressor 1 and a secondary flow inlet pipeline of the high-pressure two-stage ejector 3, and is connected with a low-pressure stage injection circulation 13 through the intercooler 4.
The operation mode of the high-pressure stage vapor compression injection cycle is as follows: the medium-temperature medium-pressure gas refrigerant from the intercooler 4 enters the high-pressure stage compressor 1 to be changed into high-temperature high-pressure gas refrigerant, then the high-pressure high-temperature refrigerant enters the condenser 2 to release heat to be changed into high-pressure liquid refrigerant, the high-pressure liquid refrigerant enters the high-pressure two-stage ejector 3 to inject the medium-temperature medium-pressure gas refrigerant from the intercooler 4 to be mixed to be changed into medium-temperature medium-pressure two-phase flow refrigerant with small-amplitude pressure rise, then the medium-temperature medium-pressure gas refrigerant enters the intercooler 4 to be subjected to gas-liquid separation, and the refrigerant.
The low-pressure stage injection circulating unit 13 is a closed loop formed by an intercooler 4, a low-pressure two-stage ejector 5, an evaporator 6, a gas-liquid separator 7, a low-pressure stage compressor 8, an electronic expansion valve E, a generator 9, a circulating pump 10a and an electromagnetic three-way valve F, a liquid outlet pipeline of the intercooler 4 is connected with a main flow inlet pipeline of the low-pressure two-stage ejector 5, an outlet pipeline of the low-pressure two-stage ejector 5 is connected with an inlet pipeline of the gas-liquid separator 7, a gas outlet of the gas-liquid separator 7 is respectively connected with an inlet pipeline of the low-pressure stage compressor 8 and a refrigerant inlet pipeline of the generator 9 through the electromagnetic three-way valve F1, an outlet pipeline of the generator 9 is connected with an inlet pipeline of the circulating pump 10a, an outlet pipeline of the low-pressure stage compressor 8 and an outlet pipeline of the circulating pump 10a are connected with an, the outlet pipeline of the evaporator 6 is connected with the 5-time flow inlet pipeline of the low-pressure double-stage ejector.
The low-pressure stage injection circulation operation mode is as follows: the middle-temperature middle-pressure liquid refrigerant flows into a low-pressure two-stage ejector 8 from an intercooler 4 to inject and flow 6 low-temperature low-pressure refrigerant from an evaporator to be mixed, the low-temperature low-pressure refrigerant is changed into two-phase flow refrigerant with small-amplitude pressure rise, then the two-phase flow refrigerant enters a gas-liquid separator 7, when interfaces a and b of an electromagnetic three-way valve F1 are connected, interfaces b and c of an electromagnetic three-way valve F2 are connected, the gas refrigerant in the gas-liquid separator 7 enters a low-pressure stage compressor 8 through an electromagnetic three-way valve F1 to be changed into high-temperature middle-pressure gas refrigerant, then the high-temperature middle-pressure gas refrigerant enters the intercooler 4 through an electromagnetic three-way valve F2 to be cooled, when the interfaces a and c of an electromagnetic three-way valve F1 are connected, the interfaces a and b of an electromagnetic three-way valve F2 are connected, the gas refrigerant in the gas-liquid separator 7 enters a generator 9 through an, the liquid refrigerant in the gas-liquid separator 7 is throttled and decompressed into low-temperature and low-pressure two-phase flow through the electronic expansion valve E, the low-temperature and low-pressure two-phase flow enters the evaporator 6 to absorb heat, and then the low-pressure refrigerant flows into the low-pressure two-stage ejector 5 from the evaporator 6 to complete one-time low-pressure stage ejection circulation.
The solar heat collection circulating unit 14 is a closed loop formed by a solar heat collector 11, a generator 9 and a circulating pump 10b which are sequentially connected, an outlet pipeline of the solar heat collector 11 is connected with a heat medium inlet pipeline of the generator 9, a heat medium outlet pipeline of the generator 9 is connected with an inlet pipeline of the circulating pump 10b, and an outlet pipeline of the circulating pump 10b is connected with an inlet pipeline of the solar heat collector 11.
The solar heat collection circulation operation mode is as follows: the heat medium absorbs heat in the solar heat collector 11 to become a high-temperature heat medium, the high-temperature heat medium flows into the generator 9 from the solar heat collector 11 to release the heat to the liquid refrigerant, the high-temperature heat medium is cooled to become a low-temperature heat medium, and the low-temperature heat medium flows to the solar heat collector 11 through the circulating pump 10b to complete a heat collecting cycle.
As shown in fig. 2, the dual-stage ejector includes a first-stage ejector and a second-stage ejector, and specifically includes a valve plate 15, a first-stage working fluid inlet 16, an injection fluid inlet 17, a first-stage receiving chamber 18, a first-stage nozzle 19, a first-stage mixing chamber 20, a first-stage pressure-expanding chamber 21, a second-stage working fluid inlet 22, a second-stage nozzle 23, a second-stage receiving chamber 24, a second-stage mixing chamber 25, and a second-stage pressure-expanding chamber 26.
The operation mode of the double-stage ejector is as follows: in the low-pressure stage injection cycle 13, the medium-temperature and medium-pressure liquid refrigerant is divided into two parts and enters the low-pressure two-stage ejector 5, the flow ratio of the two parts is adjusted by the valve plate 15, one part enters the first-stage ejector through the first-stage working fluid inlet 16, the other part enters the second-stage ejector through the second-stage working fluid inlet 22, the refrigerant is accelerated and depressurized at the throat of the first-stage nozzle 19 to become two-phase flow, then the refrigerant is jetted into the first-stage receiving chamber 18 to form a low-pressure area with lower pressure than that of the evaporator 6, the saturated vapor refrigerant from the evaporator 6 is jetted from the low-pressure area, the two-phase flow refrigerant enters the first-stage mixing chamber 20 to be fully mixed, then the refrigerant is decelerated and pressurized in the first-stage diffusion chamber 21 to enter the second-stage receiving chamber 23, the second-stage working fluid is accelerated and depressurized through the second-, then the two-phase flow refrigerant completes the pressure rise in the secondary pressure expansion chamber 26 and flows into the gas-liquid separator 7; in a high-pressure stage vapor compression injection cycle, a high-pressure gaseous refrigerant is divided into two parts and enters a high-pressure two-stage ejector 3, the flow ratio of the two parts is regulated by a valve plate 15, one part enters the first-stage ejector through a first-stage working fluid inlet 16, the other part enters a second-stage ejector through a second-stage working fluid inlet 22, the gaseous refrigerant is subjected to speed-increasing and pressure-reducing at the throat part of a first-stage nozzle 19 and is changed into two-phase flow, then the gaseous refrigerant is injected into a first-stage receiving chamber 18 to form a low-pressure area with lower pressure than that of an intercooler 4, the low-pressure area injects saturated vapor refrigerant from the intercooler 4, the two-phase flow refrigerant enters a first-stage mixing chamber 20 to be fully mixed, then the gaseous refrigerant is subjected to speed-reducing and pressure-increasing in a first-stage diffusion chamber 21 and enters a second-stage, the refrigerant is mixed well in the secondary mixing chamber 25, and then the two-phase flow refrigerant is boosted in the secondary decompression chamber 26 to flow into the intercooler 4.
In the operation of the refrigeration system, under the condition of sufficient illumination, the solar heat collection circulating unit 14 normally operates, at the moment, the interfaces a and c of the electromagnetic three-way valve F1 are connected, the interfaces a and b of the electromagnetic three-way valve F2 are connected, the low-pressure stage compressor 8 is in a closed state, and the circulating pump 10a normally operates; when the illumination is insufficient, the solar heat collection circulating unit 14 and the circulating pump 10a are in a closed state, the interfaces a and b of the electromagnetic three-way valve F1 are connected, the interfaces b and c of the electromagnetic three-way valve F2 are connected, and the low-pressure stage compressor 8 operates normally.
Claims (5)
1. The ship solar vapor compression refrigeration cycle system with the double-stage ejector is characterized by comprising a high-pressure-stage vapor compression injection cycle (12), a low-pressure-stage injection cycle (13) and a solar heat collection cycle (14) which are sequentially connected.
2. The high-pressure stage vapor compression injection cycle (12) as claimed in claim 1, wherein the condenser (2) outlet line is connected to the main flow inlet line of the high-pressure two-stage injector (3), the high-pressure two-stage injector (3) outlet line is connected to the intercooler (4) inlet line, and the intercooler (4) refrigerant gas outlet line is connected to the high-pressure stage compressor (1) inlet line and the high-pressure two-stage injector (3) secondary flow inlet line, and is connected to the low-pressure stage injection cycle (13) through the intercooler (4).
3. The low-pressure stage injection cycle (14) according to claim 1, wherein the liquid outlet pipeline of the intercooler (4) is connected to the main flow inlet pipeline of the low-pressure two-stage ejector (5), the outlet pipeline of the low-pressure two-stage ejector (5) is connected to the inlet pipeline of the gas-liquid separator (7), the gas outlet of the gas-liquid separator (7) is connected to the inlet pipeline of the low-pressure stage compressor (8) and the refrigerant inlet pipeline of the generator (9) respectively through an electromagnetic three-way valve (F1), the outlet pipeline of the generator (9) is connected to the inlet pipeline of the circulating pump (10 a), the outlet pipeline of the low-pressure stage compressor (8) and the outlet pipeline of the circulating pump (10 a) are connected to the inlet pipeline of the intercooler (4) through an electromagnetic three-way valve (F2), and the liquid refrigerant outlet pipeline of the gas-liquid separator (7), the outlet pipeline of the evaporator (6) is connected with the secondary flow inlet pipeline of the low-pressure double-stage ejector (5).
4. Solar energy collection cycle (14) according to claim 1, wherein the outlet line of the solar energy collector (11) is connected to the heat medium inlet line of the generator (9), the heat medium outlet line of the generator (9) is connected to the inlet line of the circulation pump (10 b), and the outlet line of the circulation pump (10 b) is connected to the inlet line of the solar energy collector (11).
5. The dual stage ejector according to claim 1, wherein the valve plate (15) is located between the first working fluid inlet (15) and the second working fluid inlet (22), the primary working fluid inlet (16) is connected to the primary nozzle (19), the primary nozzle (19) is located in the primary receiving chamber (18), the primary receiving chamber (18) is connected to the primary mixing chamber (20), the primary mixing chamber (20) is connected to the primary pressure expansion chamber (21), and the primary pressure expansion chamber is connected to the secondary receiving chamber (24); the secondary working fluid inlet (22) is connected with the secondary nozzle (23), the secondary nozzle (23) is positioned in the secondary receiving chamber (24), the secondary receiving chamber (24) is connected with the secondary mixing chamber (25), and the secondary mixing chamber (25) is connected with the secondary diffuser (26).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110012442.8A CN112556230B (en) | 2021-01-06 | 2021-01-06 | A ship solar vapor compression refrigeration cycle system with dual-stage ejector |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110012442.8A CN112556230B (en) | 2021-01-06 | 2021-01-06 | A ship solar vapor compression refrigeration cycle system with dual-stage ejector |
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| CN112556230A true CN112556230A (en) | 2021-03-26 |
| CN112556230B CN112556230B (en) | 2023-09-12 |
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| CN202110012442.8A Expired - Fee Related CN112556230B (en) | 2021-01-06 | 2021-01-06 | A ship solar vapor compression refrigeration cycle system with dual-stage ejector |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115076820A (en) * | 2022-08-22 | 2022-09-20 | 宁波奥克斯电气股份有限公司 | Air conditioner energy saving system, control method and air conditioner |
| CN115406217A (en) * | 2022-08-12 | 2022-11-29 | 嵊州市浙江工业大学创新研究院 | Solar vacuum freezing combined hot air drying device |
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| JP2006183586A (en) * | 2004-12-28 | 2006-07-13 | Jfe Engineering Kk | Ejector and refrigeration system |
| CN110307669A (en) * | 2019-06-22 | 2019-10-08 | 太原理工大学 | A solar energy efficiency multi-mode heating device based on compression heat pump cycle |
| CN111998568A (en) * | 2020-09-07 | 2020-11-27 | 上海海洋大学 | A solar-assisted efficiency marine refrigeration system with ejector and vortex tube |
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2021
- 2021-01-06 CN CN202110012442.8A patent/CN112556230B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| FR1506421A (en) * | 1965-10-09 | 1967-12-22 | Philips Nv | Device comprising a cold source or a heat source and a piping system |
| US3383871A (en) * | 1965-10-09 | 1968-05-21 | Philips Corp | Apparatus for transporting cold to a remote location using an expansion ejector |
| JP2004045021A (en) * | 2002-05-15 | 2004-02-12 | Denso Corp | Ejector type decompression device |
| JP2006183586A (en) * | 2004-12-28 | 2006-07-13 | Jfe Engineering Kk | Ejector and refrigeration system |
| CN110307669A (en) * | 2019-06-22 | 2019-10-08 | 太原理工大学 | A solar energy efficiency multi-mode heating device based on compression heat pump cycle |
| CN111998568A (en) * | 2020-09-07 | 2020-11-27 | 上海海洋大学 | A solar-assisted efficiency marine refrigeration system with ejector and vortex tube |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115406217A (en) * | 2022-08-12 | 2022-11-29 | 嵊州市浙江工业大学创新研究院 | Solar vacuum freezing combined hot air drying device |
| CN115406217B (en) * | 2022-08-12 | 2023-08-22 | 嵊州市浙江工业大学创新研究院 | A solar vacuum freezing combined with hot air drying device |
| CN115076820A (en) * | 2022-08-22 | 2022-09-20 | 宁波奥克斯电气股份有限公司 | Air conditioner energy saving system, control method and air conditioner |
| CN115076820B (en) * | 2022-08-22 | 2022-11-25 | 宁波奥克斯电气股份有限公司 | Air conditioner energy saving system, control method and air conditioner |
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| CN112556230B (en) | 2023-09-12 |
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