CN112556230B - 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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- CN112556230B CN112556230B CN202110012442.8A CN202110012442A CN112556230B CN 112556230 B CN112556230 B CN 112556230B CN 202110012442 A CN202110012442 A CN 202110012442A CN 112556230 B CN112556230 B CN 112556230B
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- 230000006835 compression Effects 0.000 title claims abstract description 28
- 238000007906 compression Methods 0.000 title claims abstract description 28
- 238000005057 refrigeration Methods 0.000 title claims abstract description 18
- 239000003507 refrigerant Substances 0.000 claims abstract description 61
- 239000007788 liquid Substances 0.000 claims description 34
- 238000002347 injection Methods 0.000 claims description 30
- 239000007924 injection Substances 0.000 claims description 30
- 239000012530 fluid Substances 0.000 claims description 18
- 238000009792 diffusion process Methods 0.000 claims description 12
- 230000002427 irreversible effect Effects 0.000 abstract description 3
- 238000000034 method Methods 0.000 abstract description 2
- 230000005514 two-phase flow Effects 0.000 description 19
- 238000005286 illumination Methods 0.000 description 5
- 230000009977 dual effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 238000013329 compounding Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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
- 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
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- 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
The invention aims to provide a ship solar vapor compression refrigeration cycle system with a two-stage ejector, wherein a solar jet refrigerating unit in the refrigeration cycle fully utilizes offshore solar energy to complete low-pressure stage compression of a refrigerant, so that dependence of a ship on fossil energy is reduced; the two-stage ejector has the advantages of simple structure, low input cost, difficult damage, stable operation, and effective reduction of the power consumption of the compressor by reducing the irreversible loss in the throttling process by utilizing the two-stage ejector.
Description
Technical Field
The invention relates to a refrigeration cycle system, in particular to a ship solar vapor compression refrigeration cycle system with a two-stage ejector.
Background
With the rapid development of the global maritime industry and the world's increasing importance on environmental protection, countries place higher demands on ship power equipment. The current ship equipment technology level is still in a low-efficiency stage, and according to statistics, the emission of the ship diesel engine causes about 5% -10% of atmospheric pollution in the global scope. In the face of the current shortage of energy sources and the increasingly serious environmental problems, how to reduce the emission of ship power equipment is a problem that the field of the ship needs to be continuously improved. Therefore, analyzing the problems of the refrigerating device and improving the problems, fully utilizing the renewable resources is a reliable way for reducing the energy efficiency of the existing refrigerating unit.
Solar energy resources at sea are very abundant, solar energy ships have become a research trend, and solar jet refrigeration is an effective way to fully utilize 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 current single-stage ejector has poor pressure boosting capability and low efficiency, can not well realize low-temperature refrigeration, and the adoption of the adjustable double-stage ejector can improve the operation efficiency of the system.
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, which is used for optimizing the cycle by the adjustable two-stage ejector, compounding the vapor compression cycle with the solar injection cycle and reducing the irreversible loss and the running power consumption of the cycle.
The technical scheme adopted by the invention is 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 connected in sequence.
In the scheme, the method comprises the following steps: the high-pressure-stage vapor compression injection cycle is formed by a high-pressure-stage compressor, a condenser, a high-pressure two-stage ejector and an intercooler which are sequentially connected, wherein 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, the high-pressure-stage vapor compression injection cycle is connected with a 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-stage ejector, and liquid refrigerant enters the low-pressure two-stage ejector.
The low-pressure stage injection circulation comprises 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 sequentially connected, wherein a liquid outlet pipeline of the intercooler is connected with a main flow inlet pipeline of the low-pressure two-stage injector, a liquid outlet pipeline of the low-pressure two-stage injector is connected with a gas-liquid separator inlet pipeline, a gas outlet of the gas-liquid separator is respectively connected with a low-pressure stage compressor inlet pipeline and a generator refrigerant inlet pipeline through the electromagnetic three-way valve, a generator outlet pipeline is connected with a circulating pump inlet pipeline, a low-pressure stage compressor outlet pipeline and a circulating pump outlet pipeline are connected with an intercooler inlet pipeline through the electromagnetic three-way valve, a liquid refrigerant outlet pipeline of the gas-liquid separator is connected with an evaporator inlet pipeline through the electronic expansion valve, and the evaporator outlet pipeline is connected with a secondary flow inlet pipeline of the low-pressure two-stage injector.
The solar heat collection circulation comprises a closed loop formed by a solar heat collector, a generator and a circulating pump which are sequentially connected, an outlet pipeline of the solar heat collector is connected with a heat medium inlet pipeline of the generator, an outlet pipeline of the heat medium 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 generator is shared with the low-pressure-stage jet circulation, the heat medium releases heat in the generator, and the refrigerant absorbs heat in the generator to become superheated steam.
Compared with a 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 the renewable energy source solar energy is fully utilized, and the solar heat collection circulation can replace a low-pressure stage compressor to carry out one-stage boosting on the refrigerant; when the illumination condition can not meet the working requirement of the solar heat collection circulation unit, the system starts the low-pressure stage compressor to perform primary 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 the control algorithm, and can realize better adjustment and boosting capability compared with the single-stage ejector.
The invention adopts the safety measures:
the high-pressure double-stage ejector is connected with an intercooler pipeline and is provided with a check valve to prevent the refrigerant 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 to prevent the refrigerant from flowing back to the low-pressure double-stage ejector; the low pressure stage compressor is connected to the intercooler pipe and a check valve is provided to prevent the refrigerant from flowing back to the low pressure stage compressor.
The advantages of the invention are as follows.
1. According to the refrigeration system, under the condition of sufficient illumination conditions, the solar heat collection cycle is utilized to replace a low-pressure stage compressor to perform primary compression of the refrigerant; under the condition of insufficient illumination conditions, the working mode of the low-pressure-level compressor can be switched to realize intelligent energy conservation.
2. The refrigerating system provided by the invention provides an adjustable secondary ejector, which can realize better pressure boosting capacity and adjusting capacity, reduce irreversible loss and improve the refrigerating capacity of the system.
3. In the refrigeration system, the low-temperature low-pressure refrigerant from the evaporator in the low-pressure-stage injection cycle is boosted in advance by the low-pressure two-stage ejector, so that the boosting capacity of the low-pressure injection cycle is improved.
4. According to the refrigerating system, the high-pressure-stage vapor compression injection circulation uses the high-pressure two-stage injector to throttle and recover the expansion pressure, so that the throttling loss can be reduced.
5. According to the refrigerating system, the condenser adopts a mode of introducing seawater to cool down and cool down, so that the running cost of equipment is reduced, and the running efficiency of the system is improved.
Drawings
FIG. 1 is a schematic diagram of a marine solar vapor compression refrigeration cycle system with a dual stage ejector of the present invention; the names of the main components in fig. 1 are: 1-a high pressure stage compressor; a 2-condenser; 3-high pressure dual stage injector; 4-an intercooler; 5-low pressure dual stage injector; 6-an evaporator; 7-a gas-liquid separator; 8-low pressure stage compressor; 9-generator; 10 a-a circulation pump; 10 b-a circulation pump; 11-a heat collector; 12-a high-pressure-stage vapor compression injection cycle unit; 13-a low-pressure stage injection circulation unit; 14-a solar heat collection circulation unit; e-electronic expansion valve; a C-check valve; f-electromagnetic three-way valve.
FIG. 2 is a schematic diagram of a two-dimensional structure of a dual stage injector according to the present invention; the names of the components in fig. 2 are: 15-a valve plate; 16-stage working fluid inlet; 17-an injection fluid inlet; 18-a first-stage receiving chamber; 19-stage one nozzle; 20-primary mixing chamber; 21-a first stage diffuser; 22-a secondary working fluid inlet; 23-secondary nozzle; 24-a secondary receiving chamber; 25-a secondary mixing chamber; 26-second stage diffuser.
Detailed Description
The invention will be described in detail below with reference to the drawings and the detailed description.
The solar vapor compression refrigeration cycle system with the two-stage ejector for the ship comprises 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 comprises 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 circulating pump 10a, a circulating pump 10b, a heat collector 11, an electronic expansion valve E, a check valve C and an electromagnetic three-way valve F, as shown in fig. 1.
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; the outlet pipeline of the condenser 2 is connected with the main flow inlet pipeline of the high-pressure two-stage ejector 3, the outlet pipeline of the high-pressure two-stage ejector 3 is connected with the inlet pipeline of the intercooler 4, the refrigerant gas outlet pipeline of the intercooler 4 is connected with the inlet pipeline of the high-pressure stage compressor 1 and the secondary flow inlet pipeline of the high-pressure two-stage ejector 3, and the low-pressure two-stage ejector is connected with the low-pressure injection cycle 13 through the intercooler 4.
The high-pressure vapor compression injection cycle operation mode comprises the following steps: the medium-temperature medium-pressure gaseous refrigerant from the intercooler 4 enters the high-pressure stage compressor 1 to be changed into high-temperature high-pressure gaseous 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 double-stage ejector 3 to jet the medium-temperature medium-pressure gaseous 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 two-phase flow refrigerant enters the intercooler 4 to be subjected to gas-liquid separation, and the refrigerant completes one high-pressure stage vapor compression jet cycle.
The low-pressure stage injection circulation unit 13 is a closed loop formed by an intercooler 4, a low-pressure double-stage injector 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, wherein a liquid outlet pipeline of the intercooler 4 is connected with a main flow inlet pipeline of the low-pressure double-stage injector 5, an outlet pipeline of the low-pressure double-stage injector 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 an 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 inlet pipeline of the intercooler 4 through an electromagnetic three-way valve F2, a liquid refrigerant outlet pipeline of the gas-liquid separator 7 is connected with an inlet pipeline of the evaporator 6 through the electronic expansion valve E, and an outlet pipeline of the evaporator 6 is connected with an inlet pipeline of the low-pressure double-stage injector 5.
The low-pressure stage injection cycle operation mode is as follows: the medium-temperature medium-pressure liquid refrigerant flows into the low-pressure two-stage ejector 8 from the intermediate cooler 4 to be mixed with 6 low-temperature low-pressure refrigerant from the evaporator to become small-amplitude boosted two-phase flow refrigerant, then the two-phase flow refrigerant enters the gas-liquid separator 7, when the interfaces a and b of the electromagnetic three-way valve F1 are communicated, the interfaces b and c of the electromagnetic three-way valve F2 are communicated, the gaseous refrigerant in the gas-liquid separator 7 enters the low-pressure stage compressor 8 to become high-temperature medium-pressure gaseous refrigerant through the electromagnetic three-way valve F1, then the high-temperature medium-pressure gaseous refrigerant enters the intermediate cooler 4 to be cooled through the electromagnetic three-way valve F2, when the interfaces a and c of the electromagnetic three-way valve F1 are communicated, the interfaces a and b of the electromagnetic three-way valve F2 are communicated, the gaseous refrigerant in the gas-liquid separator 7 enters the generator 9 to absorb heat to become high-temperature medium-pressure gaseous refrigerant through the electromagnetic three-way valve F1, then the high-temperature medium-pressure gaseous refrigerant enters the intermediate cooler 4 through the circulating pump 10a and the electromagnetic three-way valve F2 to be cooled, the liquid refrigerant in the gas-liquid separator 7 is throttled by the electronic expansion valve E to be cooled, then the high-temperature medium-pressure gaseous refrigerant enters the low-pressure evaporator 6 to be cooled through the electromagnetic three-way valve F2, and then the two-stage ejector 6 to be cooled, and the two-stage ejector 5 is injected into the ejector 5 to absorb heat from the low-pressure refrigerant, and the ejector 5 is cooled, and the low-pressure ejector is cooled by the ejector, and the low-pressure refrigerant ejector is cooled.
The solar heat collection circulation 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 high-temperature heat medium, the high-temperature heat medium flows into the generator 9 from the solar heat collector 11 to release heat to the liquid refrigerant, the high-temperature heat medium is cooled to low-temperature heat medium, and the low-temperature heat medium flows to the solar heat collector 11 through the circulating pump 10b to complete one heat collection cycle.
As shown in fig. 2, the two-stage ejector comprises a first-stage ejector and a second-stage ejector, and specifically comprises 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 diffusion 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 diffusion chamber 26.
The operation mode of the two-stage injector is as follows: in the low-pressure stage injection cycle 13, medium-temperature medium-pressure liquid refrigerant is divided into two parts and enters the low-pressure two-stage injector 5, the flow ratio of the two parts is regulated through the valve plate 15, one part enters the first-stage injector through the first-stage working fluid inlet 16, the other part enters the second-stage injector 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 two-phase flow enters the first-stage receiving chamber 18 to form a low-pressure area with lower pressure than the evaporator 6, the low-pressure area ejects saturated vapor refrigerant from the evaporator 6, the two-phase flow refrigerant enters the first-stage mixing chamber 20 to be fully mixed, then the two-phase flow refrigerant enters the second-stage receiving chamber 23 after the first-stage diffusion chamber 21 is accelerated and depressurized, the two-phase flow is accelerated and depressurized through the second-stage nozzle 23 to become two-phase flow, the two-phase flow from the first-stage diffusion chamber 21 is ejected into the second-stage receiving chamber 24, the refrigerant is fully mixed in the second-stage mixing chamber 25, and then the two-phase flow refrigerant is pressurized in the second-stage chamber 26 to flow into the gas-liquid separator 7; in the high-pressure vapor compression injection cycle, the high-pressure gaseous refrigerant is divided into two parts and enters the high-pressure two-stage injector 3, the flow ratio of the two parts is regulated through the valve plate 15, one part enters the first-stage injector through the first-stage working fluid inlet 16, the other part enters the second-stage injector through the second-stage working fluid inlet 22, the gaseous refrigerant is accelerated and depressurized at the throat of the first-stage nozzle 19 to become two-phase flow, then the two-phase flow enters the first-stage receiving chamber 18 to form a low-pressure area with lower pressure than that of the intercooler 4, the low-pressure area is used for injecting saturated vapor refrigerant from the intercooler 4, the two-phase flow refrigerant enters the first-stage mixing chamber 20 to be fully mixed, then the two-phase flow enters the second-stage receiving chamber 23 after the first-stage diffusion chamber 21 is accelerated and depressurized, the two-phase flow is injected into the second-stage receiving chamber 24 to inject the two-phase flow from the first-stage diffusion chamber 21 through the second-stage nozzle 23, the refrigerant is fully mixed in the second-stage mixing chamber 25, and then the two-phase flow refrigerant is completely pressurized and flows into the intercooler 4 in the second-stage diffusion chamber 26.
In the operation of the refrigeration system, under the condition of sufficient illumination, the solar heat collection circulation 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 circulation pump 10a normally operates; when the illumination is insufficient, the solar heat collection circulation unit 14 and the circulation 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 (1)
1. The solar vapor compression refrigeration cycle system of the ship with the double-stage ejector is characterized by comprising 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) which are connected in sequence; the high-pressure-stage vapor compression injection circulation unit (12) is formed by a closed loop 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 the high-pressure two-stage injector (3), an outlet pipeline of the high-pressure two-stage injector (3) is connected with an inlet pipeline of the intercooler (4), a gas refrigerant outlet pipeline of the intercooler (4) is simultaneously connected with an inlet pipeline of the high-pressure-stage compressor (1) and a secondary flow inlet pipeline of the high-pressure two-stage injector (3), and the high-pressure-stage vapor compression injection circulation unit (12) is connected with a low-pressure-stage injection circulation unit (13) through the intercooler (4); the low-pressure-stage injection circulation unit (13) comprises an intercooler (4), a low-pressure two-stage injector (5), an evaporator (6), a gas-liquid separator (7), a low-pressure-stage compressor (8), an electronic expansion valve (E), a generator (9), a first circulating pump (10 a), a first electromagnetic three-way valve (F1) and a second electromagnetic three-way valve (F2), wherein a liquid outlet pipeline of the intercooler (4) is connected with a main flow inlet pipeline of the low-pressure two-stage injector (5), an outlet pipeline of the low-pressure two-stage injector (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 first electromagnetic three-way valve (F1), a refrigerant outlet pipeline of the generator (9) is connected with an inlet pipeline of the first circulating pump (10 a), and an outlet pipeline of the low-pressure-stage compressor (8) is simultaneously connected with an outlet pipeline of the first circulating pump (10 a) through the second electromagnetic three-way valve (F2) to an inlet pipeline of the intercooler (4), and a gas outlet pipeline of the gas-liquid separator (7) is connected with a refrigerant inlet pipeline of the low-pressure-stage injector (6) through the first electromagnetic three-stage valve (F1) and the refrigerant inlet pipeline; the solar heat collection circulation unit (14) comprises a closed loop formed by a solar heat collector (11), a generator (9) and a second circulation pump (10 b) 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 second circulation pump (10 b), and an outlet pipeline of the second circulation pump (10 b) is connected with an inlet pipeline of the solar heat collector (11); the two-stage ejector comprises a first-stage ejector and a second-stage ejector, and specifically comprises 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 diffusion 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 diffusion chamber (26), wherein the valve plate (15) is positioned between the first-stage working fluid inlet (16) and the second-stage working fluid inlet (22), the first-stage working fluid inlet (16) is connected with the first-stage nozzle (19), the first-stage nozzle (19) is positioned in the first-stage receiving chamber (18), the first-stage receiving chamber (18) is connected with the first-stage mixing chamber (20), the first-stage mixing chamber (20) is connected with the second-stage diffusion chamber (21), the second-stage working fluid inlet (22) is connected with the second-stage nozzle (23), the second-stage nozzle (23) is positioned in the second-stage diffusion chamber (24), the second-stage receiving chamber (24) is connected with the second-stage mixing chamber (25), the first-stage working fluid inlet (25) is connected with the second-stage mixing chamber (25), and the second-stage mixing chamber (25) is connected with the second-stage diffusion chamber (26).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110012442.8A CN112556230B (en) | 2021-01-06 | 2021-01-06 | Ship solar vapor compression refrigeration cycle system with two-stage ejector |
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| CN202110012442.8A CN112556230B (en) | 2021-01-06 | 2021-01-06 | Ship solar vapor compression refrigeration cycle system with two-stage ejector |
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| CN112556230B true CN112556230B (en) | 2023-09-12 |
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| CN115406217B (en) * | 2022-08-12 | 2023-08-22 | 嵊州市浙江工业大学创新研究院 | Solar vacuum freezing combined hot air drying device |
| 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 |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1506421A (en) * | 1965-10-09 | 1967-12-22 | Philips Nv | Device comprising a cold source or a heat source and a piping system |
| 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 kind of solar energy synergy multi-mode heating combined equipment based on compressing hot pump circulation |
| CN111998568A (en) * | 2020-09-07 | 2020-11-27 | 上海海洋大学 | Solar-assisted synergistic marine refrigeration system with ejector and vortex tube |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4016879B2 (en) * | 2002-05-15 | 2007-12-05 | 株式会社デンソー | Ejector type decompression device |
-
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- 2021-01-06 CN CN202110012442.8A patent/CN112556230B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| 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 kind of solar energy synergy multi-mode heating combined equipment based on compressing hot pump circulation |
| CN111998568A (en) * | 2020-09-07 | 2020-11-27 | 上海海洋大学 | Solar-assisted synergistic marine refrigeration system with ejector and vortex tube |
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