EP2756253A1 - Procédé et appareil pour un système de condensation de refroidissement d'air de manière retardée et prolongée - Google Patents

Procédé et appareil pour un système de condensation de refroidissement d'air de manière retardée et prolongée

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Publication number
EP2756253A1
EP2756253A1 EP12832639.4A EP12832639A EP2756253A1 EP 2756253 A1 EP2756253 A1 EP 2756253A1 EP 12832639 A EP12832639 A EP 12832639A EP 2756253 A1 EP2756253 A1 EP 2756253A1
Authority
EP
European Patent Office
Prior art keywords
thermal storage
steam
storage material
chamber
power plant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12832639.4A
Other languages
German (de)
English (en)
Inventor
Xiaodong Xiang
Rong Zhang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tahoe Technologies Ltd
Original Assignee
Tahoe Technologies Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tahoe Technologies Ltd filed Critical Tahoe Technologies Ltd
Publication of EP2756253A1 publication Critical patent/EP2756253A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the heat dissipation rate depends on the surface area of the condenser's heat exchanger and the wind blowing speed that passes through the heat exchanger surfaces. Due to cost considerations, the heat exchanger's surfaces cannot be too large otherwise the wind speed has to be very large to achieve effective cooling. According to the aerodynamics, the power consumption of a wind-blowing machine used for dry-cooling varies as the 3rd power of the wind speed it generates. The higher the wind speed it requires, the more electricity it consumes.
  • the dry-cooling approach may consume a few percent up to more than 10 percent of the electricity that the same power plant generates.
  • This two stage (time period) method can also be applied partially, e.g., in certain embodiments, during the high temperature period, only a part of the generated latent heat is stored in thermal storage materials, and dissipated into ambient air during the cool time period; while other part is still dissipated using conventional cooling methods. This is especially useful to modify and improve existing power plants.
  • CSP concentration solar thermal power
  • the starting time of the first condensation stage to be t ls and the duration of the stage 1 to be ⁇ ; the starting time of the second heat dissipation stage from the thermal storage media to be t 2 , and the duration of stage 2 to be ⁇ 2 .
  • t 2 and ⁇ equals to ⁇ 2
  • the entire cooling process becomes a normal indirect air-cooling condensation process.
  • ti the starting time of the dissipation stage
  • ⁇ 2 is not equal to ⁇ .
  • low temperature thermal storage materials to store the latent heat of exhausted steam during the day while condensing the turbine exhaust steam into water, and then dissipate the stored thermal energy into the ambient air during the night when the ambient temperature is lower, using a wind blower to drive the ambient air through the packaged thermal storage material surface to release the latent heat stored therein into the environment.
  • low temperature phase change materials PCMs are used to store the latent heat from the exhaust steam (during At time period).
  • the stored thermal energy is then dissipated into the ambient air during the night when the ambient air temperature is lower than temperature during the day via wind blower in a pre-determined time duration ⁇ 2 .
  • time durations for the condensation stage ⁇ and the heat dissipation stage ⁇ 2 so that the heat dissipation rate can be slower than that of a typical indirect dry-cooling system.
  • the exhaust steam condensation temperature can be significantly decreased. It should be noted that for every 10°C of higher
  • condensation temperature for a steam turbine generator the heat to electricity conversion efficiency would be lower by 4.5%. This is a very significant loss of efficiency because normally a "dry-cooling" approach raises the condensation temperature up to 30°C higher than that of a "wet-cooling” approach.
  • the low temperature exhausted steam transfers its latent heat to the low temperature thermal storage media via an efficient heat exchanger while condensing the steam into water.
  • the exhaust steam condensation temperature typically a few degrees higher than the low temperature thermal storage material's phase change temperature
  • phase change material During the heat dissipation stage, the phase change material would have enough temperature difference relative to the ambient air temperature so that the stored latent heat can be dissipated into the environment, as described in detail below. This is how the new approach described herein can lead to an improvement for the heat to electricity conversion efficiency.
  • the large amount of heat exchange area of our apparatus described herein ensures that the steam can be condensed into water at close to phase change temperature during the condensation stage, and that the stored latent heat can be dissipated into the environment during the night, resulting in a drop of wind speed required for effective cooling.
  • This can reduce the electricity consumption significantly due to the third power relationship between the power needed to drive a wind blower and the wind speed that is created by that blower.
  • the device comprises a combined condensation/thermal storage chamber, the chamber comprising: one or more valved ports for receiving steam from a steam source; one or more containers containing a thermal storage material; one or more valved ports for applying a vacuum to the thermal storage chamber; one or more valved ports for introducing ambient pressure air into the chamber; one or more valved ports for removing condensed water from the chamber; and a valve system operably coupling the chamber to a source of ambient temperature air.
  • a valved port indicates that flow of fluid or gas through the port is under the control of one or more valves, however, the valves need not be located at the site of the port and can be remote (e.g., disposed between a vacuum source and a vacuum port, between a steam source and a steam port, and the like).
  • the one or more containers containing a thermal storage material is a plurality of containers each containing a thermal storage material.
  • the thermal storage material is a phase change thermal storage material (PCM).
  • PCM phase change thermal storage material
  • the thermal storage material is a liquid/solid phase change thermal storage material.
  • the thermal storage material comprises a material selected from the thermal storage materials shown in Table 2 (e.g., Na 2 CC"3 ⁇ 10H 2 O, and the like).
  • the phase change material contains glass micro fibers or nano fibers.
  • the device further comprises an apparatus to cause mixing of liquid phase thermal storage material in the containers containing the thermal storage material.
  • the containers (containing the thermal storage material(s)) are attached to a frame structure (see, e.g., Figure 3) and the apparatus comprises a motor configured to cause rotation of the structure and the attached containers.
  • the one or more valved ports for applying a vacuum to the thermal storage chamber are operably coupled to a vacuum pump.
  • the one or more valved ports for applying a vacuum to the thermal storage chamber and the one or more valved ports for introducing ambient pressure air into the chamber are controlled by separate valves. In certain embodiments the one or more valved ports for applying a vacuum to the thermal storage chamber and the one or more valved ports for introducing ambient pressure air into the chamber are controlled by the same valve(s).
  • the valve system operably coupling the chamber to a source of ambient temperature air comprises a butterfly valve (or a flange cover, or other functionally equivalent structure). In certain embodiments the source of ambient air is a fan and/or blower and/or one or more ducts configured to receive ambient wind. In certain embodiments the device is one of a plurality of the devices configured in a parallel configuration.
  • the one or more valved ports for receiving steam from a steam source are operably coupled to the low temperature steam output from a turbine (e.g. , a turbine in a power plant selected from the group consisting of a coal-fired power plant, a gas-fired power plant, a nuclear power plant, and a solar thermal power plant).
  • a turbine e.g. , a turbine in a power plant selected from the group consisting of a coal-fired power plant, a gas-fired power plant, a nuclear power plant, and a solar thermal power plant.
  • the device is sited in a desert or a non-desert region with limited water availability.
  • condensation of waste steam said system comprising a plurality of devices for steam condensation and delayed dissipation of the heat produced by the condensation, e.g. , as described herein.
  • the devices are configured in a parallel configuration, e.g., as illustrated in Figure 2.
  • the system comprises at least 10, or at least 20, or at least 30, or at least 40, or at least 50, or at least 60, or at least 70, or at least 80, or at least 90, or at least 100, or at least 150, or at least 200 of said devices.
  • the system is operably coupled to the low temperature steam output from a turbine.
  • the turbine is a turbine in a power plant ⁇ e.g., a coal- fired power plant, a gas-fired power plant, a nuclear power plant, a solar thermal power plant, etc.).
  • the system is sited in a desert or a region with limited water availability.
  • a dry-cooling methods are provided. It will be recognized that the methods, as described herein provide methods of condensing waste steam while delaying heat dissipation from said condensation; and can be used to complete a Rankine cycle at enhanced efficiency.
  • a dry-cooling condensation method comprising: receiving steam from a source of steam; condensing the steam into water while transferring the latent heat of said steam into the latent heat of a thermal storage material; and dissipating the latent heat from said thermal storage material at a later time when the ambient temperature is lower than the ambient temperature at the time the steam was condensed into water.
  • the thermal storage material is a phase change thermal storage material (PCM). In certain embodiments the thermal storage material is a liquid/solid phase change thermal storage material. In certain embodiments the thermal storage material comprises a material selected from the thermal storage materials shown in Table 2 ⁇ e.g., Na 2 CC"3 ⁇ 10H 2 O, and the like).
  • the source of steam is the steam output from a turbine. In certain embodiments the turbine is in a power plant selected from the group consisting of a coal-fired power plant, a gas-fired power plant, a nuclear power plant, and a solar thermal power plant. In certain embodiments the receiving and condensing comprises receiving and condensing during daylight hours.
  • the receiving and condensing comprises receiving and condensing peak temperature hours ⁇ e.g., between noon and 3:00 pm).
  • the dissipating comprises dissipating the latent heat from the thermal storage material during cooler hours (e.g., the late afternoon, and/or evening, and/or night).
  • the method is performed using one or more devices for steam condensation and delayed dissipation of the heat produced by the condensation, e.g. , as described herein.
  • the receiving and condensing comprises: opening said one or more valved ports for applying a vacuum to a thermal storage chamber to reduce the ambient pressure in the thermal storage chamber; opening one or more valved ports for receiving steam to introduce steam from a steam source (e.g. , a turbine) into the chamber, whereby the steam condenses transferring latent heat of steam into a thermal storage material; and operating one or more valved ports for removing condensed water from the chamber to return the condensed water to the system providing the steam.
  • a steam source e.g. , a turbine
  • the dissipating comprises: restoring the pressure in the thermal storage chamber to atmospheric pressure; operating a valve system operably coupling the chamber to a source of ambient temperature air to pass ambient temperature air through the thermal storage chamber to transfer heat from the thermal storage material to the air.
  • the passing ambient temperature air comprising operating a fan and/or blower or to force air through the chamber, and/or coupling the chamber to a duct system that channels wind through the chamber.
  • the dissipating further comprises operating an apparatus to provide mixing of fluid thermal storage material in chambers containing the fluid thermal storage material.
  • the method comprises operating a motor to rotate a structure frame to which the chambers containing the thermal storage material are attached.
  • the method is performed using a system comprising a plurality of In certain embodiments the method is performed using one or more devices for steam condensation and delayed dissipation of the heat produced by the condensation, e.g., as described herein. In certain embodiments the devices are configured in a parallel configuration. In certain embodiments substantially all of the devices in said system perform said receiving and condensing at the same time. In certain embodiments substantially all of the devices in said system perform said dissipating at the same time. In certain embodiments some of the devices perform said receiving and condensing at the same time that other devices are dissipating.
  • FIG. 1 shows a schematic diagram of the apparatus 100 operably linked to a steam source (e.g., a steam turbine 101).
  • a steam source e.g., a steam turbine 101.
  • An efficient condensing heat exchanger is used to convert the latent heat of exhausted steam (e.g., from a power plant) into the latent heat of a thermal storage medium while the exhausted steam is condensed into water during a "condensation stage".
  • the valves e.g., butterfly valves, or flange covers
  • the stored heat in thermal storage medium is dissipated into the ambient air by an air stream (wind) by a blower or other wind source.
  • steam source e.g., turbine
  • steam exhaust valve 102 that connects the steam turbine and the condensing heat exchanger/thermal storage tank
  • vacuum pump 103 that is used to pump the air inside the tank out to create a vacuum (reduced pressure) in the tank
  • vacuum valve 104 that connects the vacuum pump and the tank
  • micro pole 105 for the vacuum pathway
  • valves 106 e.g., butterfly valves, flange covers, or other functionally comparable structure(s)
  • wind blower 107 or other source of an ambient temperature air stream
  • thermal storage tank 108 e.g., a supporting base 109 for the thermal storage tank
  • packaging containers 110 e.g., pipes
  • thermal storage materials e.g., phase change materials (PCMs)
  • supporting structure 111 for the phase change material packaging pipes
  • FIG. 2 schematically illustrates another embodiment of the device, where multiple steam condensation tank/heat dissipation devices (e.g., as illustrated in Figure 1) are configured in a parallel system/structure 200 operably coupled to a steam source 201.
  • steam source e.g., turbine
  • wind path pipes 207 that connect the condensing tanks together to the source of the air stream
  • the wind blower 204 or other source of a cooling air stream
  • the valve 205 e.g., a butterfly valve, flange cover or other functionally equivalent structure
  • valve 206 e.g.
  • Vacuum pump 213 connects (e.g., is operably coupled) via vacuum valve 214 and pipe 215 connects with the main exit pipe 203. Its function is to reduce pressure in the entire parallel condensation/heat dissipation system before the turbine exhaust steam is released into the system for condensation.
  • Figure 3 illustrates a structure frame 115 in a cross section view for the packaged thermal storage pipe fixture and arrangement.
  • 110 is the cross section of the packaged thermal storage pipes;
  • 116 is the structure frame to hold the storage pipes in the storage tank.
  • the center distance between packaged pipes can be optimized to allow the air stream to pass through the pipes along the length direction of the storage tank.
  • devices are described that provide delayed and prolonged dry-cooling condensation methods that take advantage of different ambient air temperatures during the day and night to reduce energy consumption for cooling (e.g., for operating a wind blower in a dry-cooling system) while decreasing the condensation temperature of the exhaust steam so that the thermal to electricity conversion efficiency can be improved for dry-cooling.
  • a vacuum can be applied to the chamber 108 by running a vacuum pump 103 (or other source of vacuum) after opening of vacuum valve 104 of the thermal storage tank 108 via a micro pole 105.
  • Low temperature exhaust steam from a steam source 101 e.g., from a power plant turbine
  • containers 110 e.g., packaged pipes
  • thermal storage materials e.g., phase change thermal storage materials (PCMs)
  • the water drains out from the tank 108 via water path (e.g., optionally valved ports) 112 to complete the Rankin cycle for the power (e.g., electricity) generation.
  • the thermal storage material is a phase change material
  • the phase change material (PCM) thermal storage material inside containers (e.g. pipes) 110 absorbs the latent heat of steam and changes its phase from solid form into liquid form, which means the phase change material (PCM) melts and keeps (stores) the latent heat. This process comprises the " condensation stage " .
  • T w is the wall temperature for the packaging pipe, which is also very close to the exhaust steam temperature for the thermal storage material
  • T m is the phase change temperature
  • p cs (p c ) is the phase change material density in the solid state
  • y c is the heat of fusion of the phase change material (or latent heat during phase change)
  • cs is the thermal conducting coefficient for the solid state phase change material
  • V c is the total volume
  • d 0 is the diameter for the phase change material's packaging container (e.g., pipe)
  • ⁇ is the amount of latent heat for the turbine exhaust steam that needs to be condensed per hour; as defined before, and ⁇ is the time duration for the "condensation stage”
  • Qi is the total latent heat condensed during the condensation stage.
  • each storage unit comprises a cylindrical container about 5 meters in diameter and 16 meters in length, made from fiber-glass material with a steel enhancement frame structure.
  • such storage units configured in parallel, e.g., as illustrated in Figure 2, would be sufficient to condense all the exhaust steam from the 10MW CSP plant into water during 6 hours of "condensation stage", store all the latent heat into these storage tanks, and wait until in the night time to be dissipated into ambient air.
  • a vent valve 114 is opened to release the air into the tank 108 until the pressure inside the tank reaches atmospheric pressure, the two butterfly valves 106 are opened, and a fan (wind blower) 107 is started to drive the ambient cooling-air flow through the thermal storage package pipe surfaces via the spaces between the package pipes 110.
  • the ambient cooling air- flow carries the latent heat of the phase change material (PCM) from the package pipes 110 surfaces into the environment. After releasing its latent heat the phase change material (PCM) of the thermal storage medium returns to its solid form again.
  • an agitator or mixer in in order to avoid the nucleation of the phase change material (PCM) inside its container (e.g., pipe) an agitator or mixer can be provided to facilitate mixing of the PCM inside the container(s).
  • the agitator/mixer can be fixed at the bottom of the thermal storage tank 108.
  • the agitator/mixer comprises a motor 113 that can drive rotation of the heat pipes attached to structure frame 111 via for example, a helical drive 116 when the thermal storage materials are in liquid phase. As a result, this motion effectively mixes the liquid phase change thermal storage materials inside the pipes to avoid the possible nucleation and phase separation of the thermal storage medium.
  • other agitator or mixer can be provided to facilitate mixing of the PCM inside the container(s).
  • the agitator/mixer can be fixed at the bottom of the thermal storage tank 108.
  • the agitator/mixer comprises a motor 113 that can drive rotation of the heat pipes attached to structure frame 111 via for example, a helical drive 116
  • agitators/agitation systems can be contemplated. Such systems include, for example acoustic/ultrasound agitation, mechanical vibrators (e.g., piezoelectric vibrators), and the like.
  • An alternative method to avoid the possible nucleation and phase separation of the thermal storage medium is to mix super thin (e.g., 5-50 ⁇ , or 10-30 ⁇ , or 10-20 ⁇ , etc.) glass fibers (e.g., about 0.1 to about 10%, or 0.5% to about 5%, or about 1% in volume) into the phase change material inside the packing containers (e.g., pipes).
  • super thin e.g., 5-50 ⁇ , or 10-30 ⁇ , or 10-20 ⁇ , etc.
  • glass fibers e.g., about 0.1 to about 10%, or 0.5% to about 5%, or about 1% in volume
  • suitable materials will be recognized by one of skill in the art.
  • any matrix materials with low density to prevent solids from precipitating to the bottom are suitable.
  • the methods and devices described herein are particularly advantageous because of the separation of the "dry-cooling" process into the “condensation stage” and the "heat dissipation stage”.
  • the turbine exhaust steam enters the storage tank and convert its latent heat (from vapor to water) into thermal storage material's latent heat with phase change process.
  • the heat dissipation process involves entirely different heat exchange mechanism because it utilizes a forced convection process with air to dissipate the heat inside the packaged thermal storage pipes into the environment.
  • the Nusselt number Nu, Reynolds Number Re and the heat exchange coefficient h are related by:
  • the equivalent diameter of cylinder d e is expressed by: where Di is the internal diameter of the cylinder tank, while d 0 is the external diameter of the N pipes.
  • PCM phase change material
  • PCM phase change material
  • Y P C M latent heat of the phase change material (PCM), in unite of J/kg.
  • h is the convection heat transfer coefficient between air flow and outer wall of pipes, in units of W/(m 2 K);
  • A is the heat exchange area for heat dissipation processes, in units of m 2 ;
  • AT m is the average convection heat exchange temperature difference, i.e. temperature difference between the outer diameter of the main tank surface and cooling air temperature, K;
  • ⁇ 2 is the heat dissipation power for the proposed apparatus
  • C p is the specific heat at constant pressure of the air flow, in units of J/(kg K)
  • q m is the mass flow rate of the air in units of kg/s
  • ⁇ ⁇ is the temperature different of the air flow between inlet and outlet of thermal storage tank 108.
  • ⁇ ⁇ 2 ⁇ 2 which means that equation (10) equals equation (11).
  • PCM phase change material
  • PCM phase change material
  • the pipes (PCM containers) can be selected such that the outer diameter is less than:
  • N is the power of the air blower in units of W
  • S is the cross sectional area of the air duct in units of m 2
  • T is the temperature of the ambient air in units of K
  • A is the heat transfer area in units of m 2 which is the sum of all the surface areas for the thermal storage package pipe (container) outside surfaces.
  • the number of devices in such a configuration is greater than 2, more preferably greater than 3, still more preferably greater than 4, 5, or 6, in certain embodiments, greater than 10, 20, 30, 40, or 50, and in certain embodiments, greater than 75, 100, 150 or greater than 200.
  • the system can handle larger amounts of exhausted steam (for example, larger than 3.6 MWh heat capacity, as in the example storage unit described above) or sustain 24 hours of continuing operation by alternating "condensing/storage" and "heat dissipation" process with different containers.
  • Another advantage with this configuration is that the number of valves that allow ambient air to enter the tank during the dissipation cycle can be reduced significantly to lower the system cost.
  • the N containers can share two butterfly valves, one for air entering path and the other for the air exhaust path through the main pipe and parallel pipes configured as described in Figure 2.
  • one wind blower with larger operation power can be used for the entire system, further simplifying system construction and reducing cost.
  • Table 1 lists typical heat dissipation time periods required for each thermal storage tank given the ambient air temperature for a typical year for the said 10 MW CSP power plant.
  • the average ambient air temperatures for each month are for the application location in northern China. It should be noted, however, that because the ambient air temperature during the night is much lower than the phase change temperature relative to the temperature difference of T w and T m , the required At 2 is actually much shorter than At ⁇ . In other words, the "delay" is much more effective than the "prolonged", especially during the winter season.
  • Table 1 Illustrates typical heat dissipation time periods given the ambient temperature for a typical year and realistic application of the system.
  • valve 102 is closed, and valve 114 is opened to let air into the storage tank until the pressure inside the tank is at or close to outside pressure.
  • the two valves 106 in Figure 1 or valves 205 and 206 in Figure 2 are opened.
  • the blower t is turned on, or where a cooling air stream is provided by ducted ambient wind, the ducts are open.
  • the power setting of the blower depends on the ambient temperature, as illustrated in the above example and Table 1.
  • low temperature phase change materials are preferred as the thermal storage material for the delay and prolonged dry-cooling applications. Means of determining suitable parameters for the phase change materials are provided above.
  • Illustrative low temperature phase change materials believed to be suitable for the heat storage material include, but are not limited to those shown in Table 2.
  • Table 2 Illustrative low temperature phase change materials suitable for exhaust steam condensation/thermal storage applications.
  • a fan is not required.
  • the system can comprise ducts to channel ambient winds through the thermal storage system thereby reducing or avoiding the power usage required by a fan.
  • valve 104 is shown to control application of vacuum to chamber 108, while a separate valve 114 is shown to introduce atmospheric pressure air into chamber 108.
  • valve 104 can be configured to switch between a vacuum source and atmospheric pressure air thereby obviating valve 114.
  • Figure 1 also shows that in certain embodiments, the device can comprise an agitator/mixer configured to rotate perforated plates to which the chambers containing the thermal storage material are attached.
  • an agitator/mixer configured to rotate perforated plates to which the chambers containing the thermal storage material are attached.
  • numerous other configures to achieve such mixing will be recognized and available to one of skill in the art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne, selon différents modes de réalisation, des dispositifs et des procédés pour un système de condensation par refroidissement à sec amélioré. Dans certains modes de réalisation, les procédés impliquent la réception de vapeur en provenance d'une source de vapeur (p. ex., une centrale) ; la condensation de la vapeur en eau tout en transférant la chaleur latente de la vapeur dans la chaleur latente du matériau d'accumulation thermique ; et la dissipation de la chaleur latente en provenance du matériau d'accumulation thermique de manière ultérieure quand la température ambiante est inférieure à la température ambiante au moment où la vapeur a été condensée en eau.
EP12832639.4A 2011-09-12 2012-09-11 Procédé et appareil pour un système de condensation de refroidissement d'air de manière retardée et prolongée Withdrawn EP2756253A1 (fr)

Applications Claiming Priority (2)

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US201161533551P 2011-09-12 2011-09-12
PCT/US2012/054688 WO2013039926A1 (fr) 2011-09-12 2012-09-11 Procédé et appareil pour un système de condensation de refroidissement d'air de manière retardée et prolongée

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EP2756253A1 true EP2756253A1 (fr) 2014-07-23

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US (1) US20130240188A1 (fr)
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