WO2019110862A1 - Disposición mvc de bajo ratio de compresión - Google Patents
Disposición mvc de bajo ratio de compresión Download PDFInfo
- Publication number
- WO2019110862A1 WO2019110862A1 PCT/ES2018/070782 ES2018070782W WO2019110862A1 WO 2019110862 A1 WO2019110862 A1 WO 2019110862A1 ES 2018070782 W ES2018070782 W ES 2018070782W WO 2019110862 A1 WO2019110862 A1 WO 2019110862A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- vapor
- latent heat
- face
- compression ratio
- heat exchanger
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
- F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
- F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D1/00—Evaporating
- B01D1/04—Evaporators with horizontal tubes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D1/00—Evaporating
- B01D1/16—Evaporating by spraying
- B01D1/20—Sprayers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D1/00—Evaporating
- B01D1/28—Evaporating with vapour compression
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0003—Condensation of vapours; Recovering volatile solvents by condensation by using heat-exchange surfaces for indirect contact between gases or vapours and the cooling medium
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0003—Condensation of vapours; Recovering volatile solvents by condensation by using heat-exchange surfaces for indirect contact between gases or vapours and the cooling medium
- B01D5/0009—Horizontal tubes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0057—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes
- B01D5/006—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes with evaporation or distillation
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0057—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes
- B01D5/0075—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes with heat exchanging
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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
- C02F1/041—Treatment of water, waste water, or sewage by heating by distillation or evaporation by means of vapour compression
-
- 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
- C02F1/048—Purification of waste water by evaporation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
- F28D15/046—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure characterised by the material or the construction of the capillary structure
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0066—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications with combined condensation and evaporation
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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
Definitions
- the present invention relates to a desalination device by mechanical vapor compression, MVC, of low compression ratio
- the devices of desalination by mechanical vapor compression MVC or mechanical vapor re-compression MVR are based on the transformation of kinetic energy in compression work of the primary steam, to achieve an increase in pressure and temperature of the secondary vapor.
- the secondary vapor leaves the compressor and condenses on the condensing wall of a latent heat exchanger, releasing latent heat of condensation that passes through the wall of the latent heat exchanger and transforms into latent heat of evaporation on the evaporator face, generating primary steam that it is reintroduced in the compressor to generate new secondary vapor.
- a MVC is a device that recycles practically all the latent heat and the energy it consumes is basically mechanical energy to move the steam compressor. This mechanical energy is a small fraction of the enthalpy recycled in the vapor.
- the coefficient of latent heat exchange of the current heat exchangers per thin film of liquid is around 2,000W / m 2 K, and can reach 8,000W / m 2 K in vertical configurations.
- This limited coefficient of latent heat exchange implies that the current MVC require a thermal jump, high temperature gradient between the primary vapor and the secondary vapor.
- This temperature differential is multiplied in case of multi-effect MED-MVC configurations.
- the MVC devices of the state of the art are configured with temperature differentials or thermal gradients between primary vapor and secondary vapor around 5 ° C per effect, or more.
- the compression ratio, quotient between the pressure of the steam generated and the vapor pressure suctioned, for a gradient of 5 degrees is around 1, 3, that is, above 1, 2.
- MVCs are equipped with compressors, which by definition have compression ratios of 1, 2 or more. While the fans, fans, only reach compression ratios of 1, 11 and blowers, blowers move between compression ratios of 1, 11 and 1, 2.
- Another problem of the current MVC is that, when needing compression ratios higher than 1, 2, they need to incorporate steam compressors and can not work with blowers or fans. And the compressors have reduced flow rates, which limits the production capacity of distilled water of the current MVC of the state of the art due to the relatively low steam flow they can manage.
- Another problem with the current MVC is the superheating of the secondary vapor, that is to say that the mechanical compression of the vapor causes an elevation of the temperature of the saturated steam above the temperature of equilibrium between temperature and pressure. This overheating of the vapor is multiplied by increasing the pressure gradient to be achieved between the primary vapor and the secondary vapor. Overheating requires a process of elimination and involves an energy cost.
- Another problem with current MVCs is the raising of the temperature of the primary steam to have a sufficient density to achieve sufficient levels of mechanical compressor efficiency by taking better advantage of the limited volumetric flow rate of high compression ratio compressors.
- the working temperature of the primary steam is usually between 50 ° C and 65 ° C. The requirement of raising the working temperature of the primary steam imposes an energy consumption and increases the thermal insulation requirements of the installation.
- the present invention seeks to solve one or more of the problems discussed above and increase the desalination capacity and reduce the specific energy cost per unit of desalinated water by means of a MVC de-sanitizing disposition of low compression ratio as defined in the claims.
- the MVC de-sanitizing disposition of low compression ratio can work with reduced temperatures of the primary steam due to not having the steam density requirements derived from the flow limitations imposed by a compressor. So the temperature of the primary steam can drop to temperatures close to or equal to the ambient temperature of the saline to be desalinated, reducing or eliminating the contribution of energy to increase the working temperature of the primary steam
- the reduced specific energy consumption of the low compression ratio desalination system allows it to be coupled to a 100% renewable energy source, off-grid, such as wind, photovoltaic or marine.
- a modular system consisting of more than one desalination system can be realized, each of them of dimensions following a minmax formulation in which costs are minimized and benefits are maximized, to form desalination plants of greater capacity than it can provide a single desalination provision.
- Figure 1 shows a longitudinal section of a MVC device of the state of the art with a compressor
- Figure 2 shows a zigzag section of an evaporative condenser chamber with microgrooves.
- Figure 3 shows a longitudinal section of a MVC desalination device with a low compression ratio with a fan.
- Figure 1 shows in a schematic a desalination system by mechanical steam compression MVC of the state of the art that has a latent heat exchanger 1 of tubes or chambers with contribution of the saline solution on the evaporating face in fine regime descending or ascending film.
- the MVC of the state of the art may have a vertical or horizontal arrangement.
- the MVC of the state of the art has a steam compressor 4 that receives primary vapor 2 from the evaporating face of the latent heat exchanger 1 The compressor 4 raises the pressure of the primary vapor 2 generating secondary vapor 5.
- the secondary vapor 5 is supplied to the condensing face of exchanger 1 where it condenses and water condensed 6 is extracted from the device.
- the latent heat is released and this energy is transmitted through the wall of the latent heat exchanger until it reaches the evaporator face where the energy is transformed into latent heat by evaporating part of the heat.
- saline solution that is provided the evaporating face producing a brine 3 that is extracted from the device and new primary steam 2 that is reintroduced in the compressor 4, restarting a new cycle.
- the saline solution flows on the evaporator face of the heat exchanger 1 in the form of a thin film of liquid.
- the thermal resistances of the water layers limit the added latent heat transfer coefficient of the latent heat exchanger wall of the state of the art, which are around 2,000W / m 2 K, and can reach coefficients of about 6 QQ0W / m 2 K in vertical arrangements.
- the thermal resistances imposed by the layers of water make necessary a differential or temperature gradient around 5 ° C, or more, by effect.
- the secondary vapor 5 experiences a phenomenon called overheating as a result of the compression process.
- the temperature of the primary vapor increases above the equilibrium temperature in relation to its pressure. This involves the need to incorporate a de-superheater at the outlet of the condenser 4, to eliminate this overheating and the corresponding loss of energy.
- the MVC devices of the state of the art usually work at a primary steam temperature between 55 ° C and 65 ° C to have steam with the highest possible density, without exceeding 70 ° C in the secondary steam in order to avoid precipitation of salts.
- the MVC vapor compression desalination system with low compression coefficient is shown in a diagram. It can adopt a vertical configuration as in figure 3 or a horizontal configuration.
- the MVC desalination system of low compression ratio has the following specific characteristics, which differentiate it from a MVC arrangement of the state of the art:
- the condenser face of these tubes or chambers is covered, at least in part, with microgrooves or another capillary structure on which the water vapor condenses in a capillary condensation regime.
- the section, inclination and length of these micro-grooves or other capillary structure is the necessary so that, taking into account the energy flow and the rhythm of condensation, the condensed water flows inside the capillary structures and leaves a space free of layers of water between the end of the meniscus and the end of the microsurface or other capillary structure
- micro-grooves or micro-grooves on which evaporation takes place from the end of the meniscus saline solution that flows into the microgrooves or micro-grooves.
- the section, inclination and length of these micro-grooves or micro-grooves and the flow of saline solution provided within the micro-grooves or micro-grooves are the necessary so that, taking into account the energy flow and the rate of evaporation, the flow of saline solution do not dry along these micro-grooves or micro-grooves and there is a space free of layers of water between the end of the meniscus and the end of the micro-groove or micro-groove.
- the section of the wall in a configuration of these evaporator-condenser tubes or chambers 10 takes the form of a continuous broken line in a zigzag, crenellated or corrugated form. So that the thermal path 9 is free of layers of water between the capillary condensation point on the menisci of condensed water that are formed on the condenser face and the upper end of the meniscus of saline solution where evaporation occurs on the evaporator face . So the energy is transmitted without going through layers of liquid.
- the contribution of the saline solution on the evaporating face of tubes or evaporator-condenser chambers of the latent heat exchanger is carried out inside the micro-grooves or micro-grooves of the evaporator face. This contribution of saline solution is not carried out in the regime of descending water layers. Therefore, the thermal resistance of these water layers does not occur on the wall of the latent heat exchanger.
- the reduction or elimination of the thermal barriers of the water layers and the thermal efficiency of the capillary condensation and evaporation of the desalination arrangement allow the aggregate coefficient of latent heat transfer of the latent heat exchanger wall to be very high.
- the latent heat transfer coefficient of the latent heat exchangers 10 of the desalination arrangement can exceed 40,000W / m 2 K.
- the high latent heat transfer coefficient of the tubes or condenser-evaporator chambers 10, allows the low compression ratio MVC desalination device only requires a differential or temperature gradient between primary vapor and secondary vapor of between 0.8 ° C and 0.2 ° C plus the temperature differential by raising the boiling point of the saline solution.
- the temperature differential due to boiling point elevation is around 0.5 ° C.
- the temperature differential between primary steam and secondary vapor with the desalination arrangement is low, being able to be between 1, 3 ° C and 0.7 ° C, or less. That is, a temperature differential around 1 ° C, or less.
- the desalination system dedicates the reduction of the thermal gradient between primary vapor and secondary vapor to reduce the pressure differential between primary vapor and secondary vapor, which implies reducing the compression ratio or ratio between secondary vapor and primary vapor to levels below 1, 1 1
- a fan carries a cost of capital and a lower operating cost than a compressor. And the fans can move much higher flow rates than the limited volumetric flow that a compressor can move. So the cost of a fan is much lower than the cost of a compressor per unit of mass flow, and the fans allow arrangements with greater production capacity than the compressors.
- the primary steam 12 generator on the evaporator face of the heat exchanger 10 is routed through the inlet 13 of the fan 14 where the vapor pressure is increased, generating secondary vapor 15 that is supplied on the condenser side of the heat exchanger 10 high Latent heat transfer coefficient.
- the fan 14 can be configured to produce a small increase in pressure.
- An important advantage of the use of a fan 14 versus the use of a compressor 4, is that the fan 14 does not have the flow limitations that a compressor has, so that the MVC desalination arrangement of low compression ratio can be configured to increase the pressure at high steam flow rates, which allows high production capacities of distilled water.
- the fan 14 does not have the steam density requirements derived from the flow limitations imposed by a compressor, so it can work without increasing the temperature of the salt solution to be supplied to the evaporator face up to temperatures close to 65 ° C as it happens for the MVC of the state of the art to have a primary steam with a temperature of about 65 ° C with the corresponding high density.
- the fan 14 can operate at temperatures equal to or similar to the ambient temperature of the water to be desalinated, with consequent energy savings.
- the low compression ratio of the fan 14, below 1, 11, supposes lower levels of overheating than those produced with compressors with compression rails greater than 1, 2, with the consequent energy savings.
- an embodiment of the MVC desalination arrangement of low compression ratio can be designed with a temperature gradient between primary steam and secondary vapor which It can reach 0.7 ° C, or less.
- the compression ratio decreases by at levels of 1, 08 or less, and the specific energy consumption decreases so that the energy input to the MVC desalination arrangement of low compression ratio reaches the lowest levels by desalinated water unit among all industrial desalination devices, with the added advantage that this energy can be provided entirely by a renewable, off-grid source, that is, with practically no impact on the C0 2 footprint, which It involves a paradigm shift in the world of desalination and allows communities with few energy and economic resources to access safe water.
- the fan 14 can be placed inside the housing as shown in Figure 3 or it can be placed in a separate housing, connected by conduits.
- the MVC desalination system with low compression ratio can be used to desalinate sea water, brackish water or other types of salt solutions.
- the MVC desalination system of low compression ratio can be implemented in a modular configuration consisting of more than one desalination system, each of them of dimensions following a minmax formulation in which costs are minimized and benefits are maximized, to form desalination plants of greater capacity than can be provided by a single desalination facility, to provide high outputs and with connection to the network.
- the MVC desalination system with low compression ratio can be implemented under a low cost configuration designed for communities in remote or low-resource areas and that can operate 100% from renewable, off-grid energy.
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- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Life Sciences & Earth Sciences (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Sustainable Development (AREA)
- Hydrology & Water Resources (AREA)
- Environmental & Geological Engineering (AREA)
- Water Supply & Treatment (AREA)
- Organic Chemistry (AREA)
- Crystallography & Structural Chemistry (AREA)
- Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
- Heat Treatment Of Water, Waste Water Or Sewage (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Drying Of Solid Materials (AREA)
- Drying Of Gases (AREA)
- Physical Or Chemical Processes And Apparatus (AREA)
Abstract
Description
Claims
Priority Applications (16)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA3084297A CA3084297A1 (en) | 2017-12-05 | 2018-12-04 | Mechanical vapour compression arrangement having a low compression ratio |
RU2020118724A RU2772390C2 (ru) | 2017-12-05 | 2018-12-04 | Устройство механической компрессии пара, имеющее низкую степень сжатия |
JP2020530972A JP7333522B2 (ja) | 2017-12-05 | 2018-12-04 | 低圧縮比を有する機械的蒸気圧縮装置 |
EP18885762.7A EP3722726A4 (en) | 2017-12-05 | 2018-12-04 | LOW COMPRESSION RATE MVC DEVICE |
BR112020011327-1A BR112020011327A2 (pt) | 2017-12-05 | 2018-12-04 | arranjo mecânico de compressão de vapor com baixa taxa de compressão |
CN201880078474.4A CN111656123B (zh) | 2017-12-05 | 2018-12-04 | 具有低压缩比的机械蒸汽压缩装置 |
JOP/2020/0139A JOP20200139A1 (ar) | 2017-12-05 | 2018-12-04 | تجميعة ضغط بخار ميكانيكيًا ذات معدل ضغط منخفض |
SG11202005266UA SG11202005266UA (en) | 2017-12-05 | 2018-12-04 | Mechanical vapour compression arrangement having a low compression ratio |
MX2020005902A MX2020005902A (es) | 2017-12-05 | 2018-12-04 | Disposicion de compresion mecanica de vapor (mvc) de bajo ratio de compresion. |
US16/770,511 US11209217B2 (en) | 2017-12-05 | 2018-12-04 | Mechanical vapour compression arrangement having a low compression ratio |
AU2018379534A AU2018379534A1 (en) | 2017-12-05 | 2018-12-04 | Mechanical vapour compression arrangement having a low compression ratio |
PCT/ES2018/070786 WO2019110863A1 (es) | 2017-12-05 | 2018-12-05 | Disposición med-tvc de bajo ratio de compresion |
EP18885834.4A EP3722727A4 (en) | 2017-12-05 | 2018-12-05 | MULTI-EFFECT DISTILLATION WITH THERMAL VAPOR COMPRESSION (TVC-MED) WITH LOW COMPRESSION RATIO |
IL275088A IL275088A (en) | 2017-12-05 | 2020-06-03 | Mechanical vapor compression arrangement with low compression ratio |
SA520412130A SA520412130B1 (ar) | 2017-12-05 | 2020-06-04 | تجميعة تحلية مياه بالتقطير متعدد الآثار بضغط البخار الحراري ذات نسبة ضغط منخفضة |
ZA2020/03412A ZA202003412B (en) | 2017-12-05 | 2020-06-08 | Mechanical vapour compression arrangement having a low compression ratio |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ESU201731494 | 2017-12-05 | ||
ES201731494U ES1203439Y (es) | 2017-12-05 | 2017-12-05 | Cámara intercambiadora de calor latente |
ES201731521U ES1207636Y (es) | 2017-12-05 | 2017-12-13 | Dispositivo desalinizador de bajo consumo especifico |
ESU201731521 | 2017-12-13 | ||
ESPCT/ES2018/070781 | 2018-12-04 | ||
PCT/ES2018/070781 WO2019110861A1 (es) | 2017-12-05 | 2018-12-04 | Disposicion de camara intercambiadora de calor latente |
Publications (1)
Publication Number | Publication Date |
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WO2019110862A1 true WO2019110862A1 (es) | 2019-06-13 |
Family
ID=60971511
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/ES2018/070782 WO2019110862A1 (es) | 2017-12-05 | 2018-12-04 | Disposición mvc de bajo ratio de compresión |
PCT/ES2018/070781 WO2019110861A1 (es) | 2017-12-05 | 2018-12-04 | Disposicion de camara intercambiadora de calor latente |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/ES2018/070781 WO2019110861A1 (es) | 2017-12-05 | 2018-12-04 | Disposicion de camara intercambiadora de calor latente |
Country Status (15)
Country | Link |
---|---|
US (2) | US11209217B2 (es) |
EP (3) | EP3722728A4 (es) |
JP (2) | JP2021505836A (es) |
CN (2) | CN111656123B (es) |
AU (2) | AU2018381061B2 (es) |
BR (2) | BR112020011313A2 (es) |
CA (2) | CA3084297A1 (es) |
ES (3) | ES1203439Y (es) |
IL (2) | IL275088A (es) |
JO (2) | JOP20200139A1 (es) |
MX (2) | MX2020005902A (es) |
SA (3) | SA520412130B1 (es) |
SG (2) | SG11202005097SA (es) |
WO (2) | WO2019110862A1 (es) |
ZA (2) | ZA202003411B (es) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108671570A (zh) * | 2018-05-08 | 2018-10-19 | 大连理工大学 | 一种倾斜椭圆管降膜蒸发器 |
ES1250825Y (es) * | 2020-04-08 | 2020-10-28 | Wga Water Global Access Sl | Dispositivo desalinizador de compresion por inyeccion hidraulica |
WO2024052583A1 (es) * | 2022-09-08 | 2024-03-14 | Wga Water Global Access S.L. | Dispositivo desalinizador multiefecto multitren memtd |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060225863A1 (en) * | 2005-04-12 | 2006-10-12 | Alexander Levin | Heat and cold storage multistage tower with application of PCM |
JP2013088049A (ja) * | 2011-10-19 | 2013-05-13 | Mitsubishi Plastics Inc | 潜熱蓄熱槽、及び給湯システム |
US20170030656A1 (en) * | 2015-07-31 | 2017-02-02 | Sfi Electronics Technology Inc. | Thermal energy storage facility having functions of heat storage and heat release |
CN206481096U (zh) * | 2016-12-21 | 2017-09-08 | 中国科学院工程热物理研究所 | 利用可再生能源进行微细尺度换热的野外便携式电源 |
Family Cites Families (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3305454A (en) * | 1965-02-19 | 1967-02-21 | Desal Ltd | Series evaporator-tray compressor type vacuum still |
JPS5647469B2 (es) * | 1975-02-13 | 1981-11-10 | ||
AU3295378A (en) * | 1978-02-02 | 1978-07-06 | Q Dot Corp | Shaping tool for producing a wick |
JPH0794238B2 (ja) * | 1991-10-25 | 1995-10-11 | 宇宙開発事業団 | 噴霧冷却式除熱器 |
CN1065521A (zh) * | 1991-12-31 | 1992-10-21 | 吕智民 | 开式热管 |
JPH10314829A (ja) * | 1997-05-15 | 1998-12-02 | Hitachi Cable Ltd | 高温ヒートパイプ用伝熱管及び該管の製造方法 |
US6951243B2 (en) * | 2003-10-09 | 2005-10-04 | Sandia National Laboratories | Axially tapered and bilayer microchannels for evaporative coolling devices |
US7251944B2 (en) * | 2004-02-10 | 2007-08-07 | The Texas A&M University System | Vapor-compression evaporation system and method |
FR2867771B1 (fr) * | 2004-03-18 | 2006-07-21 | Int De Dessalement Soc | Procede et installation de dessalement d'eau de mer par distillation a effets multiples et thermocompression de vapeur fonctionnant avec differentes pressions de vapeur motrice |
JP2006181516A (ja) * | 2004-12-28 | 2006-07-13 | Sanyo Electric Co Ltd | 太陽光発電利用の真水生成装置 |
US20070246193A1 (en) * | 2006-04-20 | 2007-10-25 | Bhatti Mohinder S | Orientation insensitive thermosiphon of v-configuration |
AU2007307709A1 (en) * | 2006-10-10 | 2008-04-17 | Starrotor Corporation | Desalination system |
GB2443802A (en) * | 2006-11-08 | 2008-05-21 | L E T Leading Edge Technologie | Thermal desalination plant integrated upgrading process and apparatus |
CN101126613B (zh) * | 2007-09-12 | 2010-06-02 | 苏州新太铜高效管有限公司 | 冷凝器用换热管 |
WO2010026953A1 (ja) * | 2008-09-04 | 2010-03-11 | Takeda Seiichi | エネルギー効率の高い蒸留水及び/又は濃縮水の製造方法と装置 |
US20100252410A1 (en) * | 2009-03-30 | 2010-10-07 | Frederick William Millar | Water Purification Device and Method |
JP3153941U (ja) * | 2009-07-14 | 2009-09-24 | 奇宏電子深▲しん▼有限公司 | 放熱器の改良構造 |
US8292272B2 (en) * | 2009-09-04 | 2012-10-23 | Massachusetts Institute Of Technology | Water separation under reduced pressure |
CN102235615A (zh) * | 2010-04-21 | 2011-11-09 | 中国科学院工程热物理研究所 | 一种腔式发光二极管灯 |
CN202692733U (zh) * | 2012-05-09 | 2013-01-23 | 苏州新太铜高效管有限公司 | 带有吸液芯体的翅片冷凝管 |
CN202936219U (zh) * | 2012-12-12 | 2013-05-15 | 众和海水淡化工程有限公司 | 一种小型tvc-med海水淡化装置 |
CN103047891B (zh) * | 2012-12-20 | 2014-11-05 | 苏州新太铜高效管有限公司 | 网状外表面的降膜蒸发管 |
WO2015014387A1 (fr) * | 2013-07-29 | 2015-02-05 | Francois-Mathieu Winandy | Procedes et installations de dessalement d'eau par distillation a compression mecanique de vapeur |
NO340556B1 (no) * | 2014-05-30 | 2017-05-08 | Pleat As | Anordning for varmeveksling |
CN107614997B (zh) * | 2015-04-23 | 2019-08-23 | Wga水环球公司 | 冷凝器-蒸发器管 |
US10390500B2 (en) * | 2015-10-09 | 2019-08-27 | KC Harvey Environmental, LLC | Desalination membranes for subsurface irrigation |
CN105202955B (zh) * | 2015-11-16 | 2018-06-26 | 盐城市轩源加热设备科技有限公司 | 一种外部设置翅片的热管 |
US20190301808A1 (en) * | 2016-12-13 | 2019-10-03 | The Texas A&M University System | Sensible and Latent Heat Exchangers with Particular Application to Vapor-Compression Desalination |
CN107167013B (zh) | 2017-06-28 | 2018-09-25 | 天津朗华科技发展有限公司 | 一种蓄能换热装置 |
GR20170100407A (el) * | 2017-09-07 | 2019-05-09 | Αριστειδης Εμμανουηλ Δερμιτζακης | Συμπιεστης πολλαπλων θαλαμων μηχανικης επανασυμπιεσης ατμων |
US10399003B2 (en) * | 2018-02-05 | 2019-09-03 | King Fahd University Of Petroleum And Minerals | Mechanical vapor compression desalination system |
US10935325B2 (en) * | 2018-09-28 | 2021-03-02 | Microsoft Technology Licensing, Llc | Two-phase thermodynamic system having a porous microstructure sheet with varying surface energy to optimize utilization of a working fluid |
-
2017
- 2017-12-05 ES ES201731494U patent/ES1203439Y/es not_active Expired - Fee Related
- 2017-12-13 ES ES201731521U patent/ES1207636Y/es not_active Expired - Fee Related
- 2017-12-19 ES ES201731548U patent/ES1209591Y/es not_active Expired - Fee Related
-
2018
- 2018-12-04 BR BR112020011313-1A patent/BR112020011313A2/pt not_active Application Discontinuation
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- 2018-12-04 JP JP2020530972A patent/JP7333522B2/ja active Active
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- 2018-12-05 EP EP18885834.4A patent/EP3722727A4/en active Pending
-
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- 2020-06-03 IL IL275088A patent/IL275088A/en unknown
- 2020-06-03 IL IL275090A patent/IL275090A/en unknown
- 2020-06-04 SA SA520412130A patent/SA520412130B1/ar unknown
- 2020-06-04 SA SA520412132A patent/SA520412132B1/ar unknown
- 2020-06-04 SA SA520412133A patent/SA520412133B1/ar unknown
- 2020-06-08 ZA ZA2020/03411A patent/ZA202003411B/en unknown
- 2020-06-08 ZA ZA2020/03412A patent/ZA202003412B/en unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060225863A1 (en) * | 2005-04-12 | 2006-10-12 | Alexander Levin | Heat and cold storage multistage tower with application of PCM |
JP2013088049A (ja) * | 2011-10-19 | 2013-05-13 | Mitsubishi Plastics Inc | 潜熱蓄熱槽、及び給湯システム |
US20170030656A1 (en) * | 2015-07-31 | 2017-02-02 | Sfi Electronics Technology Inc. | Thermal energy storage facility having functions of heat storage and heat release |
CN206481096U (zh) * | 2016-12-21 | 2017-09-08 | 中国科学院工程热物理研究所 | 利用可再生能源进行微细尺度换热的野外便携式电源 |
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