CN111056581A - A two-stage compression heat pump seawater desalination device with combined freezing and evaporation - Google Patents
A two-stage compression heat pump seawater desalination device with combined freezing and evaporation Download PDFInfo
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- CN111056581A CN111056581A CN202010018020.7A CN202010018020A CN111056581A CN 111056581 A CN111056581 A CN 111056581A CN 202010018020 A CN202010018020 A CN 202010018020A CN 111056581 A CN111056581 A CN 111056581A
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- 239000013535 sea water Substances 0.000 title claims abstract description 176
- 238000010612 desalination reaction Methods 0.000 title claims abstract description 62
- 230000006835 compression Effects 0.000 title claims abstract description 22
- 238000007906 compression Methods 0.000 title claims abstract description 22
- 238000001704 evaporation Methods 0.000 title claims abstract description 17
- 230000008020 evaporation Effects 0.000 title claims abstract description 15
- 238000007710 freezing Methods 0.000 title claims abstract description 13
- 230000008014 freezing Effects 0.000 title claims abstract description 13
- 239000003507 refrigerant Substances 0.000 claims abstract description 171
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 57
- 239000007788 liquid Substances 0.000 claims abstract description 34
- 239000013505 freshwater Substances 0.000 claims abstract description 24
- 230000002301 combined effect Effects 0.000 claims abstract description 4
- 239000002351 wastewater Substances 0.000 claims description 28
- 239000002184 metal Substances 0.000 claims description 10
- 238000005057 refrigeration Methods 0.000 claims 2
- 239000003795 chemical substances by application Substances 0.000 claims 1
- 150000003839 salts Chemical class 0.000 abstract description 10
- 238000005516 engineering process Methods 0.000 abstract description 5
- 238000009835 boiling Methods 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 7
- 238000005265 energy consumption Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 239000012528 membrane Substances 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000011033 desalting Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000004821 distillation Methods 0.000 description 2
- 230000008018 melting Effects 0.000 description 2
- 238000002844 melting Methods 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000909 electrodialysis Methods 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000001223 reverse osmosis Methods 0.000 description 1
- 239000010865 sewage Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000004083 survival effect Effects 0.000 description 1
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- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F1/00—Treatment of water, waste water, or sewage
- C02F1/02—Treatment of water, waste water, or sewage by heating
- C02F1/04—Treatment of water, waste water, or sewage by heating by distillation or evaporation
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- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F1/00—Treatment of water, waste water, or sewage
- C02F1/02—Treatment of water, waste water, or sewage by heating
- C02F1/04—Treatment of water, waste water, or sewage by heating by distillation or evaporation
- C02F1/16—Treatment of water, waste water, or sewage by heating by distillation or evaporation using waste heat from other processes
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- C—CHEMISTRY; METALLURGY
- C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
- C02F2103/00—Nature of the water, waste water, sewage or sludge to be treated
- C02F2103/08—Seawater, e.g. for desalination
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A20/00—Water conservation; Efficient water supply; Efficient water use
- Y02A20/124—Water desalination
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- Heat Treatment Of Water, Waste Water Or Sewage (AREA)
Abstract
The invention belongs to the technical field of seawater desalination, and particularly relates to a two-stage compression heat pump seawater desalination device with freezing and evaporation combined effects; the refrigerant circulating system comprises a first compressor, a first condenser, a first throttling valve, an evaporator, a second compressor, a second condenser, a second throttling valve, a gas-liquid separator and a third heat exchanger; the first seawater desalination system comprises a first seawater tank, a first water pump and an evaporator; the second seawater desalination system comprises a second seawater tank, a second water pump, a first condenser, a second condenser, a vacuum pump, a second heat exchanger and a fresh water tank. The invention adopts a two-stage compression heat pump technology to prepare fresh water, and seawater is frozen at the evaporator side to form ice without salt; the seawater is heated at the condenser side to form vapor without salt, and the seawater is heated by the two condensers to reach the boiling point more easily and be evaporated; while the ice on the evaporator side can be melted by the refrigerant cycle.
Description
Technical Field
The invention belongs to the technical field of seawater desalination, and particularly relates to a two-stage compression heat pump seawater desalination device with combined action of freezing and evaporation.
Background
With the development of socio-economy, as essential substances on earth on which all living things are dependent on development and survival, the world's fresh water resources have become very short, and thus the rational utilization of fresh water and energy has become one of the global difficulties in the new century. The seawater desalination technology is undoubtedly one of the important ways to solve the freshwater crisis.
Currently, common methods for desalinating seawater include distillation methods, membrane technologies, and the like. The distillation method mainly adopts multi-stage flash evaporation and multi-effect flash evaporation, but has large energy consumption and high desalination cost. The seawater desalination technology by reverse osmosis and electrodialysis membrane also has the outstanding problems of large energy consumption, high membrane processing and using cost, complex desalination process and the like. Meanwhile, the common heat pump type seawater desalination device only utilizes the heat quantity at the condenser side and neglects the cold quantity at the evaporator side. Therefore, a device with high desalination efficiency, low cost and simple process is needed to meet the existing demand.
Disclosure of Invention
The invention aims to solve the problems and provides a double-effect two-stage compression heat pump seawater desalination device.
In order to achieve the technical purpose, the invention adopts the following technical scheme:
a two-stage compression heat pump seawater desalination device with freezing and evaporation combined effects comprises a refrigerant circulating system, wherein the refrigerant circulating system comprises a first compressor, a second condenser, a second throttling valve, a gas-liquid separator, a first throttling valve and an evaporator; the outlet of the first compressor is connected with the inlet of the second compressor, the outlet of the second compressor is connected with the refrigerant inlet of the second condenser, the refrigerant outlet of the second condenser is connected with the inlet of the second throttling valve, the outlet of the second throttling valve is connected with the inlet of the gas-liquid separator, the first outlet of the gas-liquid separator is connected with the inlet of the second compressor, and the second outlet of the gas-liquid separator is connected with the inlet of the first throttling valve; a first refrigerant pipeline is arranged in the evaporator, and an inlet and an outlet of the first refrigerant pipeline are respectively a first refrigerant inlet and a first refrigerant outlet; the first throttling valve outlet is connected with a first refrigerant inlet of the evaporator, and a first refrigerant outlet of the evaporator is connected with an inlet of the first compressor; the refrigerant circulating system also comprises a first condenser, the outlet of the first compressor is also connected with the inlet of the first condenser, and the refrigerant outlet of the first condenser is connected with the inlet of the first throttling valve; the system also comprises a first seawater desalination system and a second seawater desalination system, wherein the first seawater desalination system comprises a first seawater tank, a first water pump and an evaporator; the first seawater tank is communicated with a seawater channel inlet of the evaporator through a first water pump; the first seawater tank is provided with a seawater replenishing port, and the evaporator is provided with an ice discharging port and a wastewater outlet; the second seawater desalination system comprises a second seawater tank, a second water pump, a first condenser, a second condenser, a vacuum pump, a second heat exchanger and a fresh water tank; the vacuum pump enables the second seawater desalination system to be in a vacuum state, the second seawater tank is communicated with the seawater inlet of the first condenser through the second water pump, the seawater outlet of the first condenser is communicated with the seawater inlet of the second condenser, and the water vapor outlet of the second condenser is communicated with the fresh water tank sequentially through the vacuum pump and the second heat exchanger; the second seawater tank is provided with a seawater supplement port, and the second condenser is provided with a wastewater outlet.
Further, the refrigerant circulating system also comprises a third heat exchanger, and the third heat exchanger is connected with the evaporator in parallel; the outlet of the first throttling valve is also connected with the inlet of a third heat exchanger, and the outlet of the third heat exchanger is connected with the inlet of the first compressor; a second refrigerant pipeline is arranged in the evaporator, and an inlet and an outlet of the second refrigerant pipeline are respectively a second refrigerant inlet and a second refrigerant outlet; the refrigerant outlet of the second condenser is also connected with the second refrigerant inlet of the evaporator, and the second refrigerant outlet of the evaporator is connected with the outlet of the first throttling valve.
Furthermore, the first seawater desalination system also comprises a first heat exchanger, and a wastewater outlet of the evaporator is communicated with an inlet of the first heat exchanger; the first heat exchanger is positioned in the first seawater tank and is provided with a wastewater discharge pipe extending out of the first seawater tank.
Further, a first stop valve is arranged on a pipeline between the refrigerant outlet of the second condenser and the refrigerant inlet of the second condenser; the first stop valve is connected in parallel with the second throttle valve, and the second condenser refrigerant outlet is connected with the second refrigerant inlet through the first stop valve.
Further, the pipe connected with the second refrigerant outlet is provided with a third throttling valve, and the second refrigerant outlet of the evaporator is connected with the outlet of the first throttling valve through the third throttling valve.
Further, a second stop valve is arranged on a pipeline between the first throttling valve outlet and the first refrigerant inlet; the second stop valve is connected with the third heat exchanger in parallel, and the outlet of the first throttling valve is connected with the first refrigerant inlet through the second stop valve; a pipeline between the outlet of the third heat exchanger and the inlet of the first compressor is provided with a third stop valve; the third stop valve is connected with the evaporator in parallel, and the outlet of the third heat exchanger is connected with the inlet of the first compressor through the third stop valve.
Furthermore, a heat exchanger in the evaporator is a metal flat plate, the first refrigerant pipeline and the second refrigerant pipeline both penetrate through one side of the metal flat plate, and the interior of the other side of the metal flat plate is hollow to form the seawater channel.
Furthermore, the second heat exchanger and the third heat exchanger are both forced convection air-cooled fin heat exchangers.
Compared with the prior art, the invention has the beneficial technical effects that:
(1) compared with the conventional heat pump, the two-stage compression heat pump is adopted for preparing the fresh water, and in the process of preparing the fresh water, the seawater is heated by the two condensers, so that the seawater is easier to reach the boiling point and evaporate, the energy consumption can be effectively reduced, and the seawater desalination speed is improved; by recovering the latent heat of condensation at the condenser side of the heat pump, the seawater is heated at the condenser side to form vapor without salt, so that the seawater desalination is completed, and the seawater desalination speed at the condenser side is increased by the gas-liquid separator; the cold energy of the evaporator side of the heat pump is utilized to freeze the seawater to form ice without salt at the evaporator side, the seawater desalination is completed, and the seawater desalination speed at the evaporator side is increased by the gas-liquid separator;
the condenser is combined with the evaporator to jointly prepare fresh water, so that the speed of seawater desalination is increased, and the seawater desalination cost is saved;
(2) the invention can melt ice by refrigerant circulation;
(3) the waste water with low temperature and high concentration enters the first heat exchanger from the evaporator to exchange heat with the initial seawater in the first seawater tank, so that the temperature of the initial seawater is reduced, and the seawater entering the evaporator is easier to freeze.
Drawings
FIG. 1 is a connection structure diagram of a two-stage compression heat pump seawater desalination device with freezing and evaporation combined effect according to this embodiment;
fig. 2 is a structural view of the evaporator of the present embodiment.
In the figure: 1-a second compressor, 2-a first compressor, 3-an evaporator, 4-a third stop valve, 5-a third heat exchanger, 6-a second stop valve, 7-a third throttle valve, 8-a first stop valve, 9-a first throttle valve, 10-a first heat exchanger, 11-a first seawater tank, 12-a first water pump, 13-a second seawater tank, 14-a second water pump, 15-a gas-liquid separator, 16-a second throttle valve, 17-a second condenser, 18-a vacuum pump, 19-a second heat exchanger, 20-a fresh water tank, 21-a first condenser, 22-a first refrigerant inlet, 23-a first refrigerant outlet, 24-a second refrigerant inlet, 25-a second refrigerant outlet, 26-a first refrigerant pipeline, 27-second refrigerant pipe, 28-seawater channel.
Detailed Description
The invention will be further described with reference to specific examples, but the scope of the invention is not limited thereto.
As shown in fig. 1 and fig. 2, the two-stage compression heat pump seawater desalination apparatus with combined freezing and evaporating functions in this embodiment includes a refrigerant circulation system, where the refrigerant circulation system includes a first compression unit 2, a second compression unit 1, a second condenser 17, a second throttle valve 16, a gas-liquid separator 15, a first throttle valve 9, and an evaporator 3. An outlet of the first compressor 2 is connected to an inlet of the second compressor 1, an outlet of the second compressor 1 is connected to a refrigerant inlet of the second condenser 17, a refrigerant outlet of the second condenser 17 is connected to an inlet of the second throttle valve 16, an outlet of the second throttle valve 16 is connected to an inlet of the gas-liquid separator 15, a first outlet of the gas-liquid separator 15 is connected to an inlet of the second compressor 1, and a second outlet of the gas-liquid separator 15 is connected to an inlet of the first throttle valve 9. A first refrigerant pipe 26 is provided in the evaporator 3, and an inlet and an outlet of the first refrigerant pipe 26 are a first refrigerant inlet 22 and a first refrigerant outlet 23, respectively. The outlet of the first throttle 9 is connected to a first refrigerant inlet 22 of the evaporator 3, and a first refrigerant outlet 23 of the evaporator 3 is connected to the inlet of the first compressor 2. The refrigerant circulation system further includes a first condenser 21, an outlet of the first compressor 2 is further connected to an inlet of the first condenser 21, and a refrigerant outlet of the first condenser 21 is connected to an inlet of the first throttle valve 9. A part of the refrigerant flowing out of the first compressor 2 enters the first condenser 21, and the other part enters the second condenser 17 via the second compressor 1. The liquid refrigerant flowing out of the gas-liquid separator 15 joins the refrigerant flowing out of the first condenser 21, and then enters the first throttle valve 9.
The embodiment further comprises a first seawater desalination system, wherein the first seawater desalination system comprises a first seawater tank 11, a first water pump 12 and an evaporator 3. The first seawater tank 11 is communicated with the inlet of the seawater channel 28 of the evaporator 3 through the first water pump 12. The first seawater tank 11 is provided with a seawater replenishing port, and the evaporator 3 is provided with an ice discharging port and a wastewater outlet. The seawater in the first seawater tank 11 is sent to the seawater channel 28 in the evaporator 3 by the first water pump 12, ice without salt is formed and is melted, and then the ice is discharged from the ice discharge port, and high-concentration wastewater is discharged from the wastewater outlet. In the evaporator 3, the refrigerant flows in the corresponding refrigerant pipeline, the seawater flows in the seawater channel 28 outside the refrigerant pipeline, and the refrigerant transfers the cold energy to the seawater, so that the seawater is frozen on the inner wall of the seawater channel 28.
The embodiment further includes a second seawater desalination system, and the second seawater desalination system includes a second seawater tank 13, a second water pump 14, a first condenser 21, a second condenser 17, a vacuum pump 18, a second heat exchanger 19, and a fresh water tank 20. The vacuum pump 18 makes the second seawater desalination system in a vacuum state, the second seawater tank 13 is communicated with the seawater inlet of the first condenser 21 through the second water pump 14, the seawater outlet of the first condenser 21 is communicated with the seawater inlet of the second condenser 17, and the vapor outlet of the second condenser 17 is communicated with the fresh water tank 20 through the vacuum pump 18 and the second heat exchanger 19 in sequence. The second seawater tank 13 is provided with a seawater supplement port, and the second condenser 17 is provided with a wastewater outlet. The seawater in the second seawater tank 13 is sent to the first condenser 21 by the second water pump 14 to be heated, the seawater flows out of the first condenser 21 and then enters the second condenser 17 to be heated and vaporized to form water vapor without salt, the water vapor enters the second heat exchanger 19 by the vacuum pump 18 to be condensed into fresh water and then enters the fresh water tank 20, and the high-concentration wastewater is discharged from the wastewater outlet of the second condenser 17. In the first condenser 21, the refrigerant flows in the corresponding refrigerant pipe, the seawater flows in the corresponding seawater pipe, and the heat released by the refrigerant is transferred to the seawater, so that the temperature of the seawater is raised. In the second condenser 17, the refrigerant flows in the corresponding refrigerant pipe, the seawater flows in the corresponding seawater pipe, and the heat released by the refrigerant is transferred to the seawater, so that the seawater is changed into vapor.
A part of the refrigerant flowing out of the first compressor 2 enters the first condenser 21, and the other part enters the second condenser 17 via the second compressor 1. When ice is made, the refrigerant flowing out of the second condenser 17 enters the gas-liquid separator 15 through the second throttle valve 16. The gaseous refrigerant flowing out of the gas-liquid separator 15 is merged with the refrigerant flowing out of the first compressor 2 and then enters the second compressor 1, and the gaseous refrigerant separated by the gas-liquid separator 15 has higher temperature and exchanges heat with the refrigerant flowing out of the first compressor 2, so that the temperature of the refrigerant entering the second compressor 1 is increased, and the efficiency is improved. The liquid refrigerant is merged with the refrigerant flowing out of the first condenser 21 and then enters the first throttling valve 9, the refrigerant flowing out of the first throttling valve 9 enters the first refrigerant pipeline 26 in the evaporator 3, and the temperature of the liquid refrigerant separated by the gas-liquid separator 15 is low, so that the humidity of the refrigerant entering the evaporator 3 through the first throttling valve 9 is low, more heat of seawater can be absorbed, and the efficiency of the heat pump is improved. The refrigerant flows out of the first refrigerant pipe 26 and enters the first compressor 2.
In the embodiment, the two-stage compression heat pump technology is adopted to prepare the fresh water, compared with the conventional heat pump, in the process of preparing the fresh water by the two-stage compression heat pump, the seawater is heated by the two condensers, the boiling point is more easily reached and the seawater is evaporated, the energy consumption can be effectively reduced, and the seawater desalination speed is improved; by recovering the latent heat of condensation at the condenser side of the heat pump, the seawater is heated at the condenser side to form vapor without salt, so that the seawater desalination is completed, and the seawater desalination speed at the condenser side is increased by the gas-liquid separator; the cold energy of the evaporator side of the heat pump is utilized to freeze the seawater to form ice without salt at the evaporator side, the seawater desalination is completed, and the seawater desalination speed at the evaporator side is increased by the gas-liquid separator; the condenser is combined with the evaporator to jointly produce fresh water, thereby improving the speed of seawater desalination and saving the cost of seawater desalination.
The embodiment further comprises a third heat exchanger 5, the third heat exchanger 5 is connected with the evaporator 3 in parallel, an outlet of the first throttling valve 9 is further connected with an inlet of the third heat exchanger 5, and an outlet of the third heat exchanger 5 is connected with an inlet of the first compressor 2. A second refrigerant pipe 27 is provided in the evaporator 3, and an inlet and an outlet of the second refrigerant pipe 27 are a second refrigerant inlet 24 and a second refrigerant outlet 25, respectively. The refrigerant outlet of the second condenser 17 is also connected to a second refrigerant inlet 24 of the evaporator 3, and a second refrigerant outlet 25 of the evaporator 3 is connected to the outlet of the first throttle valve 9. During deicing, a part of the refrigerant flowing out of the second condenser 17 enters the gas-liquid separator 15 through the second throttle valve 16, and the other part of the refrigerant enters the second refrigerant pipeline 27 in the evaporator 3; the gaseous refrigerant flowing out of the gas-liquid separator 15 is merged with the refrigerant flowing out of the first compressor 2 and then enters the second compressor 1, the liquid refrigerant flowing out of the gas-liquid separator 15 is merged with the refrigerant flowing out of the first condenser 21 and then enters the first throttling valve 9, and the refrigerant flowing out of the first throttling valve 9 is merged with the refrigerant flowing out of the second refrigerant pipeline 27 and then flows into the first compressor 2 through the third heat exchanger 5. When de-iced, the third heat exchanger 5 acts as an evaporator to maintain the normal operation of the refrigerant cycle. Therefore, in the present embodiment, the refrigerant has different circulation circuits corresponding to ice making and ice removing, and ice can be melted by the refrigerant circulation in the process of making ice by the refrigerant circulation.
In order to recover the cold energy of the wastewater in the first seawater desalination system, the first seawater desalination system further comprises a first heat exchanger 10. The waste water outlet of the evaporator 3 is communicated with the inlet of the first heat exchanger 10. The first heat exchanger 10 is located in the first seawater tank 11, and the first heat exchanger 10 is provided with a wastewater discharge pipe extending out of the first seawater tank 11. The first heat exchanger 10 is a water-cooling heat exchanger, wastewater discharged from a wastewater outlet of the evaporator 3 enters the first heat exchanger 10, the first heat exchanger 10 is positioned in the first seawater tank 11, an outlet pipeline of the first heat exchanger 10 extends out of the first seawater tank 11, and the wastewater is discharged from the outlet pipeline of the first heat exchanger 10. The waste water with low temperature and high concentration enters the first heat exchanger 10 from the evaporator 3 to exchange heat with the initial seawater in the first seawater tank 11, so that the temperature of the initial seawater is reduced, and the seawater entering the evaporator 3 is easier to freeze.
To facilitate switching between ice making and ice removing, the conduit between the refrigerant outlet of the second condenser 17 and the second refrigerant inlet 24 is provided with a first shut-off valve 8. The first cut-off valve 8 is connected in parallel with the second throttle valve 16, and the refrigerant outlet of the second condenser 17 is connected to the second refrigerant inlet 24 through the first cut-off valve 8. During deicing, the first stop valve 8 is opened, and a part of the refrigerant flowing out of the second condenser 17 enters the second throttle valve 16, and the other part of the refrigerant flows into the second refrigerant pipe 27 of the evaporator 3 through the first stop valve 8. The conduit to which the second refrigerant outlet 25 is connected is provided with a third throttle valve 7, and the second refrigerant outlet 25 of the evaporator 3 is connected to the outlet of the first throttle valve 9 via the third throttle valve 7. The refrigerant flows out through the third throttle valve 7 and then joins the refrigerant flowing out of the first throttle valve 9, and the joined refrigerant enters the third heat exchanger 5.
In order to prevent refrigerant from entering the evaporator 3 and to let refrigerant enter the third heat exchanger 5 when de-icing is to take place, the conduit between the outlet of the first throttle 9 and the first refrigerant inlet 22 is provided with a second shut-off valve 6. The second shut-off valve 6 is connected in parallel with the third heat exchanger 5, and the outlet of the first throttle valve 9 is connected to the first refrigerant inlet 22 through the second shut-off valve 6. The conduit between the outlet of the third heat exchanger 5 and the inlet of the first compressor 2 is provided with a third stop valve 4. The third stop valve 4 is connected with the evaporator 3 in parallel, and the outlet of the third heat exchanger 5 is connected with the inlet of the first compressor 2 through the third stop valve 4. The second stop valve 6 is closed, the third stop valve 4 is opened, and the refrigerant flowing out of the first throttle valve 9 enters the first compressor 2 from the third heat exchanger 5. The second shut-off valve 6 is opened, the third shut-off valve 4 is closed, the refrigerant flowing out of the first throttle valve 9 enters the first refrigerant pipe 26 in the evaporator 3, and the refrigerant flowing out of the first refrigerant outlet 23 enters the first compressor 2.
In order to improve the heat exchange efficiency between the refrigerant in the first refrigerant pipeline 26 in the evaporator 3 and the seawater in the seawater channel 28 and simultaneously improve the heat exchange efficiency between the refrigerant in the second refrigerant pipeline 27 in the evaporator 3 and the ice blocks in the seawater channel 28, the heat exchanger in the evaporator 3 is a metal flat plate, the first refrigerant pipeline 26 and the second refrigerant pipeline 27 both penetrate through one side of the metal flat plate, and the other side of the metal flat plate is hollow to form the seawater channel 28. The metal plate has a high thermal conductivity, and the refrigerant in the first refrigerant line 26 quickly transfers cold to the seawater to freeze the seawater when ice is made. During ice melting, the refrigerant in the second refrigerant line 27 quickly transfers heat to the ice cubes to melt them. In order to enhance the heat exchange efficiency of the second heat exchanger 19 and the third heat exchanger 5, the second heat exchanger 19 and the third heat exchanger 5 are both forced convection air-cooled fin heat exchangers.
The seawater desalination process of the embodiment comprises an operation mode. In the operation mode, the first stop valve 8 and the third stop valve 4 are closed, the second stop valve 6 is opened, and the high-temperature and high-pressure gaseous refrigerant from the second compressor 1 passes through the second condenser 17 and the second throttle valve 16 to complete the first-stage throttling and change into a medium-pressure gas-liquid two-phase state; the refrigerant in gas-liquid two-phase state enters the gas-liquid separator 15, wherein the gas returns to the second compressor 1, and the liquid with more refrigerating capacity passes through the first throttle valve 9 to complete the secondary throttling to reach lower temperature and enters the evaporator 3 through the second stop valve 6. The first water pump 12 pumps seawater from the first seawater tank 11, the seawater enters the seawater channel 28 in the evaporator 3, the inner wall surface of the seawater channel 28 is frozen, and ice hardly contains salt, so the ice can be used as fresh water; meanwhile, the high-concentration wastewater is discharged from the wastewater outlet of the evaporator 3 and enters the first heat exchanger 10, and as the wastewater is cooled in the evaporator 3 and has a lower temperature, the wastewater exchanges heat with the initial seawater in the first heat exchanger 10, so that the temperature of the seawater is reduced, and the seawater is more likely to freeze after entering the evaporator 3. The second water pump 14 extracts seawater from the second seawater tank 13, the seawater enters the first condenser 21 through a pipeline, latent heat is absorbed in the first condenser 21, the temperature of the seawater is raised, then the seawater enters the second condenser 17 through the pipeline, the latent heat is reused in the second condenser 17 to evaporate the seawater, the principle that the second condenser 17 obtains fresh water is based on the principle that salt is almost insoluble in low-pressure water vapor, a vacuum pump 18 is used to keep a high vacuum degree of a second seawater desalination system during operation, then the second condenser 17 is used to heat the seawater to evaporate and vaporize the seawater under high vacuum, the obtained water vapor enters the second heat exchanger 19 through the vacuum pump 18, the seawater is condensed into fresh water and then enters the fresh water tank 20, and meanwhile, the high-concentration wastewater is discharged from a wastewater outlet of the second condenser 17.
The desalination process of seawater in this embodiment further includes a deicing mode. In the deicing mode, on the basis of the operation mode, the first stop valve 8 and the third stop valve 4 are opened, the second stop valve 6 is closed, at this time, one path of refrigerant flowing out of the refrigerant outlet of the second condenser 17 enters the second throttle valve 16, the other path of refrigerant enters the second refrigerant inlet 24 of the evaporator 3 through the first stop valve 8, ice in the seawater channel 28 in the evaporator 3 is heated, the ice is melted and falls off from the inner wall of the seawater channel 28, and then falls off from the ice discharge port at the bottom end of the evaporator 3, so that fresh water is obtained. The hot refrigerant for melting ice is returned from the second refrigerant outlet 25 of the evaporator 3 to the outlet of the first throttle valve 9 through the third throttle valve 7, meets the refrigerant at the outlet of the first throttle valve 9, and enters the third heat exchanger 5, and the third heat exchanger 5 serves as an evaporator to maintain the normal operation of the refrigerant circulation circuit. The two modes can be switched mutually, when ice blocks are formed on the heat exchange plate in the evaporator 3, the ice removing mode can be entered, ice removal is completed, and then the operation mode is returned. The embodiment can be used for desalting seawater and can also be used for desalting and extracting water in other solutions or sewage.
While the embodiments of the present invention have been described in detail, it will be apparent to those skilled in the art that variations may be made in the embodiments without departing from the spirit of the invention, and such variations are to be considered within the scope of the invention.
Claims (8)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010018020.7A CN111056581B (en) | 2020-01-08 | 2020-01-08 | Freezing evaporation combined two-stage compression heat pump sea water desalination device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010018020.7A CN111056581B (en) | 2020-01-08 | 2020-01-08 | Freezing evaporation combined two-stage compression heat pump sea water desalination device |
Publications (2)
| Publication Number | Publication Date |
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| CN111056581A true CN111056581A (en) | 2020-04-24 |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111777124A (en) * | 2020-06-18 | 2020-10-16 | 东南大学 | A photovoltaic direct-driven seawater evaporation freezing desalination system and desalination method |
| CN112158903A (en) * | 2020-09-30 | 2021-01-01 | 东南大学 | Seawater desalination device based on solution dehumidification |
| CN115028223A (en) * | 2022-08-10 | 2022-09-09 | 山东天瑞重工有限公司 | System for sea heat pump unites sea water desalination system operation |
| CN116067031A (en) * | 2023-01-17 | 2023-05-05 | 北京理工大学 | A dual-pressure evaporative self-cascading high-temperature heat pump cycle system |
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| CN205208928U (en) * | 2015-12-25 | 2016-05-04 | 徐英杰 | Big temperature rise two -stage of efficient throttle two -stage compression heat pump water heater |
| CN107010684A (en) * | 2017-04-22 | 2017-08-04 | 祝长宇 | A kind of low temperature multi-effect seawater desalting system |
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| CN1880236A (en) * | 2006-05-09 | 2006-12-20 | 青岛大学 | Sea water desalting method |
| CN102320674A (en) * | 2011-06-08 | 2012-01-18 | 集美大学 | Marine cold and heat cogeneration seawater desalting method and equipment |
| CN205208928U (en) * | 2015-12-25 | 2016-05-04 | 徐英杰 | Big temperature rise two -stage of efficient throttle two -stage compression heat pump water heater |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111777124A (en) * | 2020-06-18 | 2020-10-16 | 东南大学 | A photovoltaic direct-driven seawater evaporation freezing desalination system and desalination method |
| CN112158903A (en) * | 2020-09-30 | 2021-01-01 | 东南大学 | Seawater desalination device based on solution dehumidification |
| CN112158903B (en) * | 2020-09-30 | 2022-03-04 | 东南大学 | Seawater desalination device based on solution dehumidification |
| CN115028223A (en) * | 2022-08-10 | 2022-09-09 | 山东天瑞重工有限公司 | System for sea heat pump unites sea water desalination system operation |
| CN115028223B (en) * | 2022-08-10 | 2022-11-01 | 山东天瑞重工有限公司 | System for sea heat pump unites sea water desalination system operation |
| CN116067031A (en) * | 2023-01-17 | 2023-05-05 | 北京理工大学 | A dual-pressure evaporative self-cascading high-temperature heat pump cycle system |
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