EP3006880A1 - Diviseur d'écoulement pour condenseur à refroidissement d'air modulaire - Google Patents

Diviseur d'écoulement pour condenseur à refroidissement d'air modulaire Download PDF

Info

Publication number
EP3006880A1
EP3006880A1 EP15188845.0A EP15188845A EP3006880A1 EP 3006880 A1 EP3006880 A1 EP 3006880A1 EP 15188845 A EP15188845 A EP 15188845A EP 3006880 A1 EP3006880 A1 EP 3006880A1
Authority
EP
European Patent Office
Prior art keywords
flow
conduit
air cooled
flow divider
diffusion region
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Withdrawn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
EP15188845.0A
Other languages
German (de)
English (en)
Inventor
Francis Badin
Christophe Deleplanque
Fabien Fauconnier
Thomas Van Quickelberghe
François VAN RECHEM
Michel Vouche
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.)
SPG Dry Cooling Belgium SPRL
Original Assignee
SPX Cooling Technologies Inc
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 SPX Cooling Technologies Inc filed Critical SPX Cooling Technologies Inc
Publication of EP3006880A1 publication Critical patent/EP3006880A1/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/02—Auxiliary systems, arrangements, or devices for feeding steam or vapour to condensers
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers

Definitions

  • the present invention relates to a mechanical draft cooling tower that utilizes air cooled condenser modules.
  • the aforementioned cooling tower operates by mechanical draft and achieves the exchange of heat between two fluids such as atmospheric air, ordinarily, and another fluid which is usually steam or an industrial process fluid or the like.
  • the aforementioned cooling tower employs flow dividers that allow for the industrial process fluid to be flowed to multiple tube bundles located in the condenser modules efficiently and economically.
  • Cooling towers are heat exchangers of a type widely used to emanate low grade heat to the atmosphere and are typically utilized in electricity generation, air conditioning installations and the like. In a mechanical draft cooling tower for the aforementioned applications, airflow is induced or forced via an air flow generator such as a driven impeller, driven fan or the like. Cooling towers may be wet or dry. Dry cooling towers can be either "direct dry,” in which steam is directly condensed by air passing over a heat exchange medium containing the steam or an "indirect dry” type cooling towers, in which the steam first passes through a surface condenser cooled by a fluid and this warmed fluid is sent to a cooling tower heat exchanger where the fluid remains isolated from the air, similar to an automobile radiator.
  • Dry cooling has the advantage of no evaporative water losses. Both types of dry cooling towers dissipate heat by conduction and convection and both types are presently in use. Wet cooling towers provide direct air contact to a fluid being cooled. Wet cooling towers benefit from the latent heat of vaporization which provides for very efficient heat transfer but at the expense of evaporating a small percentage of the circulating fluid.
  • the condenser typically requires a large surface area to dissipate the thermal energy in the gas or steam and oftentimes may present several challenges to the design engineer. It sometimes can be difficult to efficiently and effectively direct the steam to all the inner surface areas of the condenser because of nonuniformity in the delivery of the steam due to system ducting pressure losses and velocity distribution. Therefore, uniform steam distribution is desirable in air cooled condensers and is critical for optimum performance. Another challenge or drawback is, while it is desirable to provide a large surface area, steam side pressure drop may be generated thus increasing turbine back pressure and consequently reducing efficiency of the power plant.
  • cooling tower performance i.e. the ability to extract an increased quantity of waste heat in a given surface
  • cost-effective methods of manufacture and assembly also improve the overall efficiency of cooling towers in terms of cost-effectiveness of manufacture and operation. Accordingly, it is desirable for cooling tower that are efficient in both in the heat exchange properties and assembly. The present invention addresses this desire.
  • Embodiments of the present invention advantageously provides for a fluid, usually steam and method for a modular mechanical draft cooling tower for condensing said steam.
  • a flow divider for the distribution of a flow of industrial fluid for use in an air cooled condenser or the like having a vertical axis, the flow divider comprising: a cylindrical lower base portion that receives the flow of industrial fluid; an upper diffusion region that extends from said cylindrical base portion wherein said upper diffusion region is generally non-cylindrical in geometry; a first port disposed on said upper diffusion region that allows for the flow of industrial fluid there through; and a first conduit connected to said first port.
  • an air cooled condenser for cooling an industrial fluid comprising: a first condenser bundle having a first set of tubes having first and second ends; a steam manifold connected to the third ends of the first set tubes; a condensate header connected to said fourth end of the first set tubes; a second condenser bundle having a second set of tubes having third and fourth ends; a steam manifold connected to the first ends of the second set tubes; a condensate header connected to said second end of the second set tubes; a flow divider for the distribution of a flow of industrial comprising: a cylindrical lower base portion that is receives the flow of industrial fluid; an upper diffusion region that extends from said cylindrical base portion wherein said upper diffusion region is generally non-cylindrical in geometry; a first port disposed on said upper diffusion region that allows for the flow of industrial fluid there through; a second port disposed on said upper diffusion region that allows for the flow of industrial fluid there through and a first conduit connected to said first port
  • a method for distributing a fluid to be cooled using a flow divider comprising: receiving the fluid to be cooled through a cylindrical lower base portion that; flowing the fluid to be cooled through an upper diffusion region that extends from said cylindrical base portion wherein said upper diffusion region is generally non-cylindrical in geometry; flowing the fluid to be cooled through a first port disposed on said upper diffusion region; and flowing the fluid to be cooled through a first conduit connected to said first port.
  • a multi-delta air cooled condenser for cooling an industrial fluid or the like, comprising: a first street that comprises a first air cooled condenser module; a second street comprising a second air cooled condenser module; a first central duct that is in fluid communication with said first air cooled condenser module and said second air cooled condenser module; a third street comprising a third air cooled condenser module; a second central duct that is in fluid communication with said third air cooled condenser module; a first flow divider connected to said first central duct, comprising: a cylindrical lower base portion that receives the flow of industrial fluid; an upper diffusion region that extends from said cylindrical base portion wherein said upper diffusion region is generally non-cylindrical in geometry; a first port disposed on said upper diffusion region that allows for the flow of industrial fluid there through; and a first conduit connected to said first port, wherein said first conduit is in fluid communication with said first air
  • a quick connection coupling for use with an air cooled condenser comprising: a collar having a first half and; a second half hingedly connected to said first half; an internal sealing piece having a circumference that is disposed within said first half and said second half; a sealing member that encircles the circumference; and a releasable attachment member that releasably attaches said first half to said second half.
  • a method of retaining a first conduit and a second conduit wherein each conduit has a flange comprising: inserting the first and second conduit into a connection coupling, comprising: a collar having a first half; a second half hingedly connected to said first half; an internal sealing piece having a circumference that is disposed within said first half and said second half; a sealing member that encircles the circumference; and a releasable attachment member that releasably attaches said first have to said second half; encircling each conduit with the internal sealing piece; engaging each flange with the first half and the second half such that the conduits are retained; and tightening the attachment member such that the collar sealingly retains the conduits.
  • a flow divider for the distribution of a flow of industrial fluid for use in an air cooled condenser or the like having a vertical axis
  • the flow divider comprising: a cylindrical lower base portion that provides an inlet that receives the flow of industrial fluid, wherein said cylindrical base portion has a first diameter; a first truncated cone extending from said lower base portion wherein said first truncated cone has a first end and a second end and wherein said first truncated cone transitions from one diameter to another as said cone extends from said first end to said second end; a second truncated cone extending from said lower base portion wherein said second truncated cone has a third end and a fourth end and wherein said second truncated cone transitions from one diameter to another as said cone extends from said third end to said fourth end; a first conduit connected to said first truncated cone, wherein said first conduit has a second diameter; and a second conduit connected
  • an air cooled condenser for cooling an industrial fluid comprising: a first condenser bundle having a first set of tubes having first and second ends; a steam manifold connected to the first ends of the first set tubes; a condensate header connected to said second end of the first set tubes; a second condenser bundle having a second set of tubes having first and second ends; a steam manifold connected to the first ends of the second set tubes; a condensate header connected to said second end of the second set tubes; a flow divider, comprising: a cylindrical lower base portion that provides an inlet that receives the flow of industrial fluid, wherein said cylindrical base portion has a first diameter; a first truncated cone extending from said lower base portion wherein said first truncated cone has a first end and a second end and wherein said first truncated cone transitions from one diameter to another as said cone extends from said first end to said second end; a second trunc
  • a method of retaining a first conduit and a second conduit wherein each conduit has a flange comprising: inserting the first and second conduit into a connection coupling, comprising: a collar having a first half; a second half hingedly connected to said first half; an internal sealing piece having a circumference that is disposed within said first half and said second half; a sealing member that encircles the circumference; and a releasable attachment member that releasably attaches said first have to said second half; encircling each conduit with the internal sealing piece; engaging each flange with the first half and the second half such that the conduits are retained; and tightening the attachment member such that the collar sealingly retains the conduits.
  • FIG. 1 a sectional view of a series of air cooled condenser modules of an air cooled condenser, generally designated 10, is illustrated.
  • the air cooled condenser modules 10 include multiple A-type geometry deltas, each designated 12 and 14 respectively. Two deltas are identified for ease of description and explanation however the condenser modules employ numerous deltas depending upon the size of the air cooled condenser tower and/or the application of the air cooled condenser tower.
  • Each delta 12, 14 comprises two tube bundle assemblies 15 having a series of finned tubes to conduct heat transfer. The deltas 12, 14 will be discussed in further detail below.
  • the flow divider 32 functions to feed four finned tube bundles 15 (two bundles per delta 12, 14).
  • the flow divider 32 comprises a base portion, generally designated 35, from which a series of conduits 24, 26, 28, 30 extend. Each conduit 24, 26, 28, 30 has a curved "elbow" shape design and connects to a respective feed conduit 16, 18, 20, 22. Each of the feed conduits 16, 18, 20, 22 is connected to, and in fluid communication with, the A-type deltas 12, 14, and more specifically, the finned tube bundles 15.
  • the flow divider 32 is comprised of two portions or regions having geometries or designs distinct from one another.
  • the flow divider 32 has a lower cylindrical base portion or region 34 wherein the main flow of the industrial fluid enters said fluid divider 32.
  • the lower base portion or region 34 transitions to a diffusion region 36 which has a generally square geometry.
  • the diffusion section 36 includes several holes or ports that coincide with the elbow conduits 24, 26, 28, 30 wherein each allows for the flow of industrial fluid there through.
  • a typical air cooled condenser employs risers to which each flow divider 32 is connected and accordingly allows flow of industrial fluid, such as steam, there through.
  • the risers are connected to a main steam duct of the air cooled condenser.
  • the flow divider 32 functions to divide and/or merge the flows of the industrial fluid by switching inlet and outlet conduits extending from said divider 32.
  • the divider 32 may have any number of dividing or merging flows depending upon the size and application of the divider 32.
  • the flow divider 32 may employ guiding vanes within the base portion 34 and/or the diffusion region 36 which assist the reduction of head loss.
  • the elbow conduits may vary in design and geometry. For example, some embodiments may employ standard elbow conduits, or short elbow conduits or mitered elbow conduits. Alternatively, "T" piece or "Y" fork designs may be utilized.
  • each delta 12, 14 is comprised of two individual heat exchange bundle assemblies 15, each having a series of finned tubes.
  • the individual tubes are approximately two (2) meters in length whereas the bundle length is approximately twelve (12) meters.
  • each bundle assembly 15 is positioned at an angle to one another to form the A-type configuration of the delta 12, 14. While the bundle assemblies 15 may be positioned at any desired angle, they preferably are positioned at an angle approximately twenty degrees (20°) to approximately thirty degrees (30°) from vertical and approximately sixty degrees (60°) to approximately seventy degrees (70°) from horizontal. More specifically, the bundle assemblies 15 are positioned at twenty-six degrees (26°) from vertical and sixty-four degrees (64°) from horizontal.
  • Each of the bundle assemblies 15 may be assembled prior to shipping wherein each typically comprises a riser to header transition piece, steam manifold, finned tubes, and steam condensate headers.
  • the embodiments of the current invention can utilize five (5) times the tubes, and also employ condenser tubes that are much shorter in length.
  • the steam velocity traveling through the tube bundles 15 is reduced as result of the increased number of tubes in combination with the reduced tube length, and therefore steam pressure drop within the deltas 12, 14 is reduced, making the air cool condenser 10 more efficient.
  • FIG. 4 an alternative embodiment of the flow divider is depicted, generally designated 40.
  • the flow divider design depicted in FIGS. 1-3 employs four elbow conduits 24, 26, 28, 30, the flow divider 40 depicted in FIG. 4 employs two elbow conduits 46, 48.
  • the flow divider has a lower cylindrical base portion or region 42 wherein the main flow of the industrial fluid enters said fluid divider 40.
  • the lower base portion or region 42 transitions to a diffusion region 44, similar to that described in connection with FIGS. 1-3 , having a geometry that is generally rectangular in design.
  • the diffusion section 44 includes two holes or ports that coincide with elbow conduits 46, 48 and allow for flow of industrial fluid there through.
  • FIGS. 5-7 plan views of alternative geometric configurations of flow dividers 50 are depicted.
  • the elbow flow conduits, generally 52 may be oriented in multiple configurations as desired or needed per the air cooled condenser application.
  • FIG. 5 illustrates the flow conduits 52 in a symmetrical orientation, parallel to one another whereas
  • FIG. 6 illustrates the flow conduits 52 positioned equidistant from one another about the flow divider 54.
  • FIG. 7 depicts a non-symmetrical orientation.
  • the flow conduits may be non-symmetrical in diameter wherein in one embodiment of the present invention, the size of the conduits may be smaller in diameter whereas other conduits may be larger in diameter.
  • FIG. 8 a schematic view of street arrangements, generally designated 60, for an air cooled condenser is illustrated in accordance with an embodiment of the present invention.
  • FIG. 8 depicts a top view for an even number of streets, 62 64, 66, 68
  • FIG. 9 illustrates an air cooled condenser set up having an odd number which will be discussed in more detail below.
  • the streets 62, 64, 66, 68 are comprised of a series of cooling modules or cells 70.
  • the cooling modules 70 are connected to, and in fluid communication with, the central duct 72 and 73 which flows industrial process fluid to the modules 70 to be cooled.
  • the modules 70 comprise of multiple A-type geometry deltas similar to those discussed in connection with FIG. 1 .
  • Each delta 12, 14 comprises two tube bundle assemblies 15 (See FIG.1 ) with a series of finned tubes to conduct heat transfer. Not shown is the process feeding the process fluid to the central duct 72, 73 such as exhaust steam from steam turbines.
  • the fluid to be cooled flows to each cell 70 via the central duct 72, 73 as previously described.
  • the industrial fluid such as turbine exhaust, is distributed to the central duct 72, 73 which is typically suspended under the air cooled condenser fan deck level.
  • the central duct 72, 73 feeds the two streets 62, 64 and 66, 68 as indicated by the arrows through a series of risers and flow dividers, similar to those described in connection with Fig. 2 .
  • the flow dividers which are designated schematically by reference numeral 74, function to feed four (4) finned tube bundles 15 (two bundles per delta 12, 14) as discussed in connect with FIGS. 1-3 .
  • each flow divider 74 comprises a base portion, from which a series of four conduits extend where two conduits feed one module 70, one conduit for each side of the A-type geometry delta, and the two other conduits feed the opposing cell, again, one conduit for each side of the A-type geometry delta.
  • each conduit has a curved "elbow" shape design and connects to a respective feed conduit.
  • Each of the feed conduits is connected to, and in fluid communication with the A-type deltas, and more specifically, the finned tube bundles.
  • Each of the flow dividers 74 is composed to two portions or regions having geometries or designs distinct from one another as previously discussed and described.
  • the fluid flow divider 74 has a lower cylindrical base portion or region 34 wherein the main flow of the industrial fluid enters said fluid divider 74.
  • the lower base portion or region 34 transitions to a diffusion region which has a generally square geometry. This diffusion section includes several holes or ports that coincide with the elbow conduits and allow for flow of industrial fluid there through.
  • FIG. 9 depicts a schematic plan view of an air cooled condenser 80 having an odd or non-even number of streets 82, 84, 86.
  • the streets 82, 84, 86 are comprised of a series of cooling modules or cells 70 similar to those discussed in connection with FIG. 8 .
  • the cooling modules 70 are connected to, and in fluid communication with, the central duct 88 and 90 which flows industrial process fluid to the modules 70 to be cooled.
  • the modules comprise of multiple A-type geometry deltas as discussed in connection with FIG. 1 .
  • Each delta 12, 14 comprises two tube bundle assemblies 15 with a series of finned tubes to conduct heat transfer.
  • the cooling modules 70 are connected to, and in fluid communication with, the central duct 88, 90 that flows industrial process fluid to the modules 70 to be cooled (See FIG. 1 ).
  • the modules include multiple A-type geometry deltas as discussed in connection with FIG. 1 .
  • Each delta 12, 14 comprises two tube bundle assemblies 15 with a series of finned tubes to conduct heat transfer. Not shown is the process feeding the process fluid to the central duct 88, 90 such as exhaust steam from steam turbines.
  • the fluid to be cooled flows to each module 70 via the central duct 88, 90 as previously described.
  • the industrial fluid such as turbine exhaust, is distributed to the central duct 88, 90 which is typically suspended under the air cooled condenser fan deck level.
  • the central duct 88 feeds streets 84 and 86, while the central duct 90 feeds streets 82 and 84 as indicated by the arrows.
  • the aforementioned flow is achieved through a series of risers and flow dividers, similar to those described in connection with Figs. 3 and 4 .
  • the flow dividers which are designated schematically at the intersection of the central ducts and the arrows, reference numerals 92 and 94.
  • the flow dividers designated with reference numeral 92 feed two streets, streets 84 and 86 or streets 82 and 84 whereas the flow dividers 94 feed a single street.
  • each comprises a base portion, generally designated 35, from which a series of conduits 24, 26, 28, 30 extend.
  • Each conduit 24, 26, 28, 30 has a curved "elbow" shape design and connects to a respective feed conduit 16, 18, 20, 22.
  • Each of the feed conduits 16, 18, 20, 22 is connected to, and in fluid communication with the A-type deltas 12, 14, and more specifically, the finned tube bundles 15.
  • the flow divider 92 is composed to two portions or regions having geometries or designs distinct from one another.
  • the flow divider 92 has a lower cylindrical base portion or region 34 wherein the main flow of the industrial fluid enters said flow divider 92.
  • the lower base portion or region 34 transitions to a diffusion region 36 which has a generally square geometry.
  • the diffusion section 36 includes several holes or ports that coincide with the elbow conduits 24, 26, 28, 30 and allow for flow of industrial fluid there through.
  • a typical air cooled condenser employs risers to which the flow divider 32 is connected and accordingly allows flow of industrial fluid, such as steam, there through.
  • the risers are connected to a main steam duct.
  • the flow divider 92 functions to divide and/or merge the flows by switching inlet and outlet conduits extending from said divider 92.
  • the divider 92 may have any number of dividing or merging flows depending upon the size and application.
  • the flow divider 92 may employ guiding vanes within the base portion 34 and/or diffusion region 36 which assist the reduction of head loss.
  • the elbow conduits may vary in design and geometry. For example, some embodiments may employ standard elbow conduits, or short elbow conduits or mitered elbow conduits.
  • the flow dividers designated by the reference numeral 94 are similar to the embodiment illustrated in FIG. 4 and will be described in connection with FIG. 4 .
  • the flow divider design depicted in FIGS. 1-3 employs four elbow conduits 24, 26, 28, 30, the flow divider 40 depicted in FIG. 4 employs two elbow conduits 46, 48.
  • the flow divider 92 has a lower cylindrical base portion 42 or region wherein the main flow of the industrial fluid enters said flow divider 92.
  • the lower base portion or region 42 transitions to a diffusion region 44, having a geometry that is generally rectangluar in design.
  • the diffusion section 44 includes two holes or ports that coincide with elbow conduits 46, 48 and allow for flow of industrial fluid there through.
  • the steam distribution has been adapted such the central ducts 88, 90 have the same diameter.
  • the central ducts operate to feed steam to one street of one side of the central duct and half of the street on the on the other side of the central duct. Therefore, one central duct is feeding two modules each of the central duct and then alternating to one module each of side and so on and so forth.
  • the quick connection includes a collar 210 and an internal sealing piece 212 that rests in, and is secured by the collar 210.
  • the internal sealing piece 212 is generally circular in diameter and has a sealing component 214 such as an O-ring or the like, which provides sealing engagement between two conduits which will be discussed in further detail below.
  • the collar 210 includes two halves or pieces 216, 218 connected via a swivel or hinge 220 at one end of the collar.
  • the collar 210 also includes a sealing attachment of each side at the other end via an attachment mechanism 222. This attachment 222 is adjustable and in one embodiment, a nut and bolt combination is preferred.
  • turbine back pressure of the air cooled condenser or the like is limited by the maximum steam velocity in the tubes (to limit erosion) wherein the steam velocity is increasing with a decrease of back pressure (due to density of steam).
  • the steam is still maintained at the maximum allowable steam velocity but at a lower back pressure.
  • Another limitation the current delta design addresses is that the pressure at the exit of the secondary bundles cannot be less than the vacuum pump capability. This pressure typically results from turbine back pressure minus the pressure drop in ducting minus the pressure drop in the tubes. Accordingly, due to the reduced pressure drop in the tubes, the allowable turbine back pressure is lower with the propose air cooled condenser design.
  • the above-described bundle design also reduces the pressure drop within the individual delta 12, 14.
  • the heat exchange that takes place via the deltas 12, 14, is dependent upon the heat exchange coefficient, i.e., the mean temperature difference between air and steam and the exchange surface. Due to the reduced pressure drop as previously described, the mean pressure (average between inlet pressure and exit pressure) in the exchanger is higher with the design of the proposed air cooled condenser. In other words, because steam is saturated, the mean steam temperature is also higher for the same heat exchange surface resulting in increased heat exchange.
  • alternative embodiment bundles may not include a manifold prior to shipping. More specifically, in such embodiments, the tube bundles may be ship without steam manifolds attached thereto. In said embodiments, the tube bundles may be assembled in field to form the A-type configuration, as discussed above. However, instead of employing two steam manifolds, this alternative embodiment may employ a single steam manifold wherein the single steam manifold extends along the "apex" of the A configuration.
  • the flow divider 300 has a main cylindrical portion or base 302 that provides a flow inlet.
  • the flow divider 300 also comprises first and second flow branches each connected to, and extending from, the main cylindrical portion 302.
  • the flow branches 304, 306 as illustrated have a geometry similar to truncated cone regions, 304 and 306 respectively, having a first region having a first diameter that transitions to a second region having a smaller diameter. As can be seen in FIGS.
  • the flow branch portions 304, 306 may alternatively be described as a melding or combination or merger of flow regions having a "T" geometry and a "Y" geometry.
  • the flow divider 300 includes cylindrical portions, 308 and 310, attached to a respective branch 304, 306. Said cylindrical portions 308, 310 have a diameter that is less than the diameter of the inlet portion 302.
  • the above-described design requires less manufacture time, while also providing a lighter design allowing for less fluid side pressure drop.
  • This present solution should also be more easily cut in piece and re-welded on site. Therefore, the current piece should be easily manufactured as it is constructed from simple pieces.
  • the above-described divider 200 design minimizes steam side pressure drops during operation of an air cooled condenser or the like.
  • Design A is a standard "T" shape design currently used in the art whereas Design B is another "T” shaped design that utilizes flow vanes whereas Design C is the flow divider 300 of the present invention.
  • Design C or the flow divider 300 providing significant improvement steam side pressure drop wherein it demonstrated 33 percent relative to the pressure loss coefficient, K for Design A.
  • Design B demonstrated 90 percent relative to the pressure loss coefficient, K for Design A.
  • Table 1 Flow Divider Connection Design A Design B Design C C CFD - RESULTS References Conditions K - 0.730 0.654 0.239 Relative % 100% 90% 33%
EP15188845.0A 2014-10-08 2015-10-07 Diviseur d'écoulement pour condenseur à refroidissement d'air modulaire Withdrawn EP3006880A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US14/509,687 US20160102895A1 (en) 2014-10-08 2014-10-08 Modular air cooled condenser flow converter apparatus and method

Publications (1)

Publication Number Publication Date
EP3006880A1 true EP3006880A1 (fr) 2016-04-13

Family

ID=54288690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15188845.0A Withdrawn EP3006880A1 (fr) 2014-10-08 2015-10-07 Diviseur d'écoulement pour condenseur à refroidissement d'air modulaire

Country Status (5)

Country Link
US (3) US20160102895A1 (fr)
EP (1) EP3006880A1 (fr)
KR (1) KR20160042183A (fr)
CN (1) CN105509501A (fr)
AU (1) AU2015238776A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017202730A1 (fr) * 2016-05-25 2017-11-30 Spx Dry Cooling Belgium Générateur à condensateur refroidi par air et procédé
BE1024229B1 (fr) 2017-10-31 2019-05-27 Hamon Thermal Europe S.A. Unité de refroidissement, installation et procédé
CN116877381A (zh) * 2023-09-07 2023-10-13 山西常村大成节能科技有限公司 一种具有节能改造功能的空压机及使用方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951440A (en) * 1973-09-27 1976-04-20 Escher Wyss Limited Pipe branch piece
DE10330659B3 (de) * 2003-07-08 2004-12-23 Gea Energietechnik Gmbh Abdampfleitung für Dampfkraftanlagen
CN2914006Y (zh) * 2005-12-26 2007-06-20 关晓春 电站用直接空冷凝汽器倒半u形蒸汽分配装置
US20130333349A1 (en) * 2012-05-31 2013-12-19 Evapco, Inc. Turbine exhaust duct design for air cooled condensers
CN103939927A (zh) * 2014-04-28 2014-07-23 中国能源建设集团广东省电力设计研究院 烟风道及其三合一汇流管
CN103939928A (zh) * 2014-04-28 2014-07-23 中国能源建设集团广东省电力设计研究院 烟风道及其四合一汇流管

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2107478A (en) * 1934-10-17 1938-02-08 Happel Otto Air-cooled surface condenser
US2255442A (en) * 1939-02-09 1941-09-09 Farquhar Company Ltd Ab Distributor
US3223152A (en) * 1962-12-27 1965-12-14 Gea Luftkuhler Ges M B H Surface condenser
DE1776130A1 (de) * 1968-09-25 1970-10-01 Borsig Gmbh Luftgekuehlter Kondensator
US5407274A (en) * 1992-11-27 1995-04-18 Texaco Inc. Device to equalize steam quality in pipe networks
EP0646747A1 (fr) * 1993-09-17 1995-04-05 Ck Metals, Ltd. Structure de raccord de tuyaux
DE10033691A1 (de) * 2000-07-11 2002-01-24 Alstom Power Nv Kondensatorhals zwischen einer Dampfturbine und einem Kondensator
US7086131B2 (en) * 2004-05-14 2006-08-08 Victaulic Company Deformable mechanical pipe coupling
US8297344B2 (en) * 2008-07-10 2012-10-30 Spx Cooling Technologies, Inc. Modular air-cooled condenser apparatus and method
DE102012201129A1 (de) * 2012-01-26 2013-08-01 Areva Np Gmbh Vorrichtung zur Separation eines Fluid-Massenstroms
US9551532B2 (en) * 2012-05-23 2017-01-24 Spx Dry Cooling Usa Llc Modular air cooled condenser apparatus and method

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3951440A (en) * 1973-09-27 1976-04-20 Escher Wyss Limited Pipe branch piece
DE10330659B3 (de) * 2003-07-08 2004-12-23 Gea Energietechnik Gmbh Abdampfleitung für Dampfkraftanlagen
CN2914006Y (zh) * 2005-12-26 2007-06-20 关晓春 电站用直接空冷凝汽器倒半u形蒸汽分配装置
US20130333349A1 (en) * 2012-05-31 2013-12-19 Evapco, Inc. Turbine exhaust duct design for air cooled condensers
CN103939927A (zh) * 2014-04-28 2014-07-23 中国能源建设集团广东省电力设计研究院 烟风道及其三合一汇流管
CN103939928A (zh) * 2014-04-28 2014-07-23 中国能源建设集团广东省电力设计研究院 烟风道及其四合一汇流管

Also Published As

Publication number Publication date
KR20160042183A (ko) 2016-04-18
AU2015238776A1 (en) 2016-04-28
US20160102895A1 (en) 2016-04-14
CN105509501A (zh) 2016-04-20
US20160102917A1 (en) 2016-04-14
US20160102918A1 (en) 2016-04-14

Similar Documents

Publication Publication Date Title
US11662146B2 (en) Modular air cooled condenser apparatus and method
US9777963B2 (en) Method and system for radial tubular heat exchangers
US10161683B2 (en) Dry cooling system for powerplants
US10648740B2 (en) Mini-tube air cooled industrial steam condenser
KR102597977B1 (ko) 모두 부차적인 공랭식 산업용 증기 응축기
US10132568B2 (en) Dry cooling system for powerplants
EP3006880A1 (fr) Diviseur d'écoulement pour condenseur à refroidissement d'air modulaire
US20140027097A1 (en) Heat Exchanger for an Intercooler and Water Extraction Apparatus
SE519051C2 (sv) Anordning vid röranslutning för värmeväxlare

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20160905

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SPX DRY COOLING BELGIUM

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SPG DRY COOLING BELGIUM

17Q First examination report despatched

Effective date: 20190903

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20200114