WO2017005727A1 - Agencement de tube dans un évaporateur horizontal à passage unique - Google Patents

Agencement de tube dans un évaporateur horizontal à passage unique Download PDF

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Publication number
WO2017005727A1
WO2017005727A1 PCT/EP2016/065793 EP2016065793W WO2017005727A1 WO 2017005727 A1 WO2017005727 A1 WO 2017005727A1 EP 2016065793 W EP2016065793 W EP 2016065793W WO 2017005727 A1 WO2017005727 A1 WO 2017005727A1
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WO
WIPO (PCT)
Prior art keywords
tubes
tube
evaporator
once
row
Prior art date
Application number
PCT/EP2016/065793
Other languages
English (en)
Inventor
Suresh Kotachary SHENOY
Jeffrey Frederick MAGEE
Original Assignee
General Electric Technology Gmbh
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 General Electric Technology Gmbh filed Critical General Electric Technology Gmbh
Priority to JP2018500533A priority Critical patent/JP2018524547A/ja
Priority to EP16739053.3A priority patent/EP3320261A1/fr
Priority to KR1020187003894A priority patent/KR20180030095A/ko
Priority to CN201680052482.2A priority patent/CN107923609A/zh
Publication of WO2017005727A1 publication Critical patent/WO2017005727A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B17/00—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane
    • F22B17/10—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane built-up from water-tube sets in abutting connection with two sectional headers each for every set, i.e. with headers in a number of sections across the width or height of the boiler
    • F22B17/12—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane built-up from water-tube sets in abutting connection with two sectional headers each for every set, i.e. with headers in a number of sections across the width or height of the boiler the sectional headers being in vertical or substantially vertical arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B17/00—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • 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
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the present disclosure relates generally to a heat recovery steam generator (HRSG), and more particularly, to a tube arrangement for controlling flow in an HRSG having inclined tubes for heat exchange.
  • HRSG heat recovery steam generator
  • a heat recovery steam generator is an energy recovery heat exchanger that recovers heat from a hot gas stream. It produces steam that can be used in a process (cogeneration) or used to drive a steam turbine (combined cycle).
  • Heat recovery steam generators generally comprise four major components - the economizer, the evaporator, the superheater and the water preheater.
  • natural circulation HRSG's contain evaporator heating surface, a drum, as well as the necessary piping to facilitate the appropriate circulation ratio in the evaporator tubes.
  • a once-through HRSG replaces the natural circulation components with once-through evaporator and in doing so offers in-roads to higher plant efficiency and furthermore assists in prolonging the HRSG lifetime in the absence of a thick-walled drum.
  • the HRSG comprises vertical heating surfaces in the form of a series of vertical parallel flow paths/tubes 104 and 108 (disposed between the duct walls 111) configured to absorb the required heat.
  • a working fluid e.g., water
  • the working fluid is transported to an inlet manifold 105 from a source 106.
  • the working fluid is fed from the inlet manifold 105 to an inlet header 112 and then to a first heat exchanger 104, where it is heated by hot gases from a furnace (not shown) flowing in the horizontal direction.
  • the hot gases heat tube sections 104 and 108 disposed between the duct walls 111.
  • a portion of the heated working fluid is converted to a vapor and the mixture of the liquid and vaporous working fluid is transported to the outlet manifold 103 via the outlet header 113, from where it is transported to a mixer 102, where the vapor and liquid are mixed once again and distributed to a second heat exchanger 108.
  • This separation of the vapor from the liquid working fluid is undesirable as it produces temperature gradients and efforts have to be undertaken to prevent it.
  • the second heat exchanger 108 is used to overcome thermodynamic limitations.
  • the vapor and liquid are then discharged to a collection vessel 109 from which they are then sent to a separator 110, prior to being used in power generation equipment (e.g., a turbine).
  • the use of vertical heating surfaces thus has a number of design limitations
  • a once-through evaporator comprising an inlet manifold; one or more inlet headers in fluid communication with the inlet manifold; one or more tube stacks, where each tube stack comprises one or more inclined evaporator tubes; the one or more tube stacks being in fluid communication with the one or more inlet headers; where the inclined tubes are inclined at an angle of less than 90 degrees or greater than 90 degrees to a vertical; where each tube stack comprises a plurality of tubes arranged in a plurality of columns and a plurality of rows; where a plurality of tubes in a first column are offset from a plurality of tubes in a second column by a distance d2 and where a plurality of tubes in a first row are offset from a plurality of tubes in a second row by a distance dl; where dl varies from 0.1 d2 to 1000d2 to suit the optimal degree of heat blending; one or more outlet headers in fluid communication with one or more tube stacks; and an outlet manifold in
  • a method comprising discharging a working fluid through a once-through evaporator; where the once- through evaporator comprises an inlet manifold; one or more inlet headers in fluid communication with the inlet manifold; one or more tube stacks, where each tube stack comprises one or more inclined evaporator tubes; the one or more tube stacks being in fluid communication with the one or more inlet headers; where the inclined tubes are inclined at an angle of less than 90 degrees or greater than 90 degrees to a vertical; where each tube stack comprises a plurality of tubes arranged in a plurality of columns and a plurality of rows; where a plurality of tubes in a first column are offset from a plurality of tubes in a second column by a distance d2 and where a plurality of tubes in a first row are offset from a plurality of tubes in a second row by a distance dl; where dl varies from 0.1 d2 to 1000d2 to suit the optimal degree of heat blending; one
  • Figure 1 is a schematic view of a prior art heat recovery steam generator having vertical heat exchanger tubes
  • Figure 2 depicts a schematic view of an exemplary once-through evaporator that uses a counterflow staggered arrangement
  • Figure 3 depicts an exemplary embodiment of a once-through evaporator
  • Figure 4(A) depicts one exemplary arrangement of the tubes in a tube stack of a once- through evaporator
  • Figure 4(B) depicts an isometric view of an exemplary arrangement of the tubes in a tube stack of a once-through evaporator
  • Figure 5 depicts an end-on schematic view of a counterflow staggered arrangement of tubes in a tube stack in a once-through evaporator
  • Figure 6A is an expanded end-on view of a tube stack of the Figure 4.
  • Figure 6B is a depiction of a plane section taken within the tube stack of the Figure 5 A and depicts a staggered tube consideration;
  • Figure 7A depicts an elevation end-on view of tubes that are inclined in one direction while being horizontal in another direction; the tubes are arranged in a staggered fashion;
  • Figure 7B is a depiction of a plane section taken within the tube stack of the Figure 6A and depicts a staggered tube configuration
  • Figure 8 depicts that the spacing between successive tube stacks can be varied.
  • Figure 9 depicts a once-through evaporator having 10 vertically aligned zones or sections that contain tubes through which hot gases can pass to transfer their heat to the working fluid.
  • a heat recovery steam generator that comprises a single heat exchanger or a plurality of heat exchangers whose tubes are arranged to be "non- vertical".
  • HRSG heat recovery steam generator
  • the tubes are inclined at an angle to a vertical.
  • inclined it is implied that the individual tubes are inclined at an angle less than 90 degrees or greater than 90 degrees to a vertical line drawn across a tube.
  • the tubes can be horizontal in a first direction and inclined in a second direction that is perpendicular to the first direction.
  • the heating surfaces - also called finned tubes - are generally horizontally disposed.
  • the heating surfaces may be staggered as a result of which the prevailing heat transfer mode is also staggered.
  • Such an arrangement is not limited by thermal head, no remixing of the heated fluid is generally used, nor is there a temperature gradient as depicted with the vertically disposed once through heat exchanger.
  • the staggering may result from angular variations in the tube as shown in the Figure 2 below. These angular variations in the tube along with the angle of inclination are shown in the Figure 2.
  • the Figure 2 shows a section of a tube that is employed in a tube stack of the once-through evaporator. The tube stack shows that the tube is inclined to the vertical in one or more directions.
  • the tube in the Figure 2 is shown to be inclined in two directions, it can be inclined in only one direction if desired.
  • the tube is inclined in one direction at an angle of ⁇ 1 to the vertical, while it is inclined in a second direction at an angle of ⁇ 2 to the vertical.
  • ⁇ 1 and ⁇ 2 can vary by up to 90 degrees to the vertical. If the angle of inclination ⁇ 1 and ⁇ 2 are equal to 90 degrees, then the tube is stated to be substantially horizontal. If on the other hand only one angle ⁇ 1 is 90 degrees while the other angle ⁇ 2 is less than 90 degrees or greater than 90 degrees, then the tube is said to be horizontal in one direction while being inclined in another direction.
  • both ⁇ 1 and ⁇ 2 are less than 90 degrees or greater than 90 degrees, which implies that the tube is inclined in two directions. It is to be noted that by “substantially horizontal” it is implies that the tubes are oriented to be approximately horizontal (i.e., arranged to be parallel to the horizon within ⁇ 2 degrees). For tubes that are inclined, the angle of inclination ⁇ 1 and/or ⁇ 2 generally vary from about 55 degrees to about 88 degrees with the vertical. In an exemplary embodiment, it is desirable for the tube to be inclined to the vertical in at least one direction.
  • the section (or plurality of sections) containing the horizontal tubes is also termed a "once-through evaporator", because when operating in subcritical conditions, the working fluid (e.g., water, ammonia, or the like) is converted into vapor gradually during a single passage through the section from an inlet header to an outlet header. Likewise, for supercritical operation, the supercritical working fluid is heated to a higher temperature during a single passage through the section from the inlet header to the outlet header.
  • the working fluid e.g., water, ammonia, or the like
  • the supercritical working fluid is heated to a higher temperature during a single passage through the section from the inlet header to the outlet header.
  • the once-through evaporator (hereinafter “evaporator”) comprises parallel tubes that are disposed non-vertically in at least one direction that is perpendicular to the direction of flow of heated gases emanating from a furnace or boiler.
  • the Figures 3, 4(A), 4(B) and 10 depicts an exemplary embodiment of a once-through evaporator.
  • the Figure 3 depicts a plurality of vertical tube stacks in a once-through evaporator 200. In one embodiment, the tube stacks are aligned vertically so that each stack is either directly above, directly under, or both directly above and/or directly under another tube stack.
  • the Figure 4(A) depicts one exemplary arrangement of the tubes in a tube stack of a once-through evaporator; while the Figure 4(B) depicts an isometric view of an exemplary arrangement of the tubes in a tube stack of a once- through evaporator;
  • the evaporator 200 comprises an inlet manifold 202, which receives a working fluid from an economizer (not shown) and transports the working fluid to a plurality of inlet headers 204(n), each of which are in fluid communication with vertical tube stacks 210(n) comprising one or more tubes that are substantially horizontal.
  • the fluid is transmitted from the inlet headers 204(n) to the plurality of tube stacks 210(n).
  • the plurality of inlet headers 204(n), 204(n+l) and 204(n+n'), depicted in the figures are collectively referred to as 204(n).
  • the plurality of tube stacks 210(n), 210(n+l), 210(n+2) and 210(n+n') are collectively referred to as 210(n) and the plurality of outlet headers 206(n), 206(n+l), 206(n+2) and 206(n+n') are collectively referred to as 206(n).
  • multiple tube stacks 210(n) are therefore respectively vertically aligned between a plurality of inlet headers 204(n) and outlet headers 206(n).
  • Each tube of the tube stack 210(n) is supported in position by a plate 250 (see Figure 4(B)).
  • the working fluid upon traversing the tube stack 210(n) is discharged to the outlet manifold 208 from which it is discharged to the superheater.
  • the inlet manifold 202 and the outlet manifold 208 can be horizontally disposed or vertically disposed depending upon space requirements for the once-through evaporator. From the Figures 3 and 4(A), it may be seen that when the vertically aligned stacks are disposed upon one another, a passage 239 is formed between the respective stacks. A baffle system 240 may be placed in these passages to prevent the by-pass of hot gases. This will be discussed later.
  • the hot gases from a source travel perpendicular or transverse to the direction of the flow of the working fluid in the tubes 210.
  • a source e.g., a furnace, boiler or turbine
  • the hot gases travel away from the reader into the plane of the paper, or towards the reader from the plane of the paper.
  • the hot gases travel counterflow to the direction of travel of the working fluid in the tube stack. Heat is transferred from the hot gases to the working fluid to increase the temperature of the working fluid and to possibly convert some or all of the working fluid from a liquid to a vapor. Details of each of the components of the once-through evaporator are provided below.
  • the inlet header comprises one or more inlet headers 204(n), 204(n+l) and (204(n) (hereinafter represented generically by the term “204(n)”), each of which are in operative communication with an inlet manifold 202.
  • each of the one or more inlet headers 204(n) are in fluid communication with an inlet manifold 202.
  • the inlet headers 204(n) are in fluid communication with a plurality of horizontal tube stacks 210(n), 210(n+l), 210(n'+2) and 210(n) respectively ((hereinafter termed "tube stack” represented generically by the term "210(n)").
  • Each tube stack 210(n) is in fluid communication with an outlet header 206(n).
  • the outlet header thus comprises a plurality of outlet headers 206(n), 206(n+l), 206(n+2) and 206(n), each of which is in fluid communication with a tube stack 210(n), 210(n+l), 210(n+2). and 210(n) and an inlet header 204(n), 204(n+l), (204(n+2). and 204(n) respectively.
  • n is an integer value
  • ⁇ ' can be an integer value or a fractional value
  • n' can thus be a fractional value such as 1/2, 1/3, and the like.
  • valves and control systems having the reference numeral n' do not actually exist in fractional form, but may be downsized if desired to accommodate the smaller volumes that are handled by the fractional evaporator sections.
  • the once-through evaporator can comprise 2 or more inlet headers in fluid communication with 2 or more tube stacks which are in fluid communication with 2 or more outlet headers.
  • the once-through evaporator can comprise 3 or more inlet headers in fluid communication with 3 or more tube stacks which are in fluid communication with 3 or more outlet headers. In another embodiment, the once-through evaporator can comprise 5 or more inlet headers in fluid communication with 5 or more tube stacks which are in fluid communication with 5 or more outlet headers. In yet another embodiment, the once-through evaporator can comprise 10 or more inlet headers in fluid communication with 10 or more tube stacks which are in fluid communication with 10 or more outlet headers. There is no limitation to the number of tube stacks, inlet headers and outlet headers that are in fluid communication with each other and with the inlet manifold and the outlet manifold. Each tube stack is sometimes termed a bundle or a zone.
  • the Figure 9 depicts another exemplary assembled once-through evaporator.
  • the Figure 9 shows a once-through evaporator of the Figure 3 having 10 vertically aligned tube stacks 210(n) that contain tubes through which hot gases can pass to transfer their heat to the working fluid.
  • the tube stacks are mounted in a frame 300 that comprises two parallel vertical support bars 302 and two horizontal support bars 304.
  • the support bars 302 and 304 are fixedly attached or detachably attached to each other by welds, bolts, rivets, screw threads and nuts, or the like.
  • rods 306 Disposed on an upper surface of the once-through evaporator are rods 306 that contact the plates 250. Each rod 306 supports the plate and the plates hang (i.e., they are suspended) from the rod 306.
  • the plates 250 are locked in position using clevis plates.
  • the plates 250 also support and hold in position the respective tube stacks 210(n).
  • only the uppermost tube and the lowermost tube of each tube tack 210(n) is shown as part of the tube stack.
  • the other tubes in each tube stack are omitted for the convenience of the reader and for clarity's sake.
  • each rod 306 holds or supports a plate 250, the number of rods 306 are therefore equal to the number of the plates 250.
  • the entire once-through evaporator is supported and held-up by the rods 306 that contact the horizontal rods 304.
  • the rods 306 can be tie-rods that contact each of the parallel horizontal rods 304 and support the entire weight of the tube stacks. The weight of the once-through evaporator is therefore supported by the rods 306.
  • Each section is mounted onto the respective plates and the respective plates are then held together by tie rods 300 at the periphery of the entire tube stack.
  • a number of vertical plates support these horizontal heat exchangers. These plates are designed as the structural support for the module and provide support to the tubes to limit deflection.
  • the horizontal heat exchangers are shop assembled into modules and shipped to site. The plates of the horizontal heat exchangers are connected to each other in the field.
  • the Figure 5 depicts one possible arrangement of the tubes in a tube stack.
  • the Figure 5 is an end-on view that depicts two tube stacks that are vertically aligned.
  • the tube stacks 210(n) and 210(n+l) are vertically disposed on one another and are separated from each other and from their neighboring tube stacks by baffles 240.
  • the baffles 240 prevent non-uniform flow distribution and facilitate staggered and counterflow heat transfer.
  • the baffles 240 do not prevent the hot gases from entering the once-through device. They facilitate distribution of the hot gases through the tube stacks.
  • each tube stack is in fluid communication with a header 204(n) and 204(n+l) respectively.
  • the tubes are supported by metal plates 250 that have holes through which the tubes travel back and forth.
  • the tubes are serpentine i.e., they travel back and forth between the inlet header 204(n) and the outlet header 206(n) in a serpentine manner.
  • the working fluid is discharged from the inlet header 204(n) to the tube stack, where it receives heat from the hot gas flow that is perpendicular to the direction of the tubes in the tube stack.
  • the Figure 6 A is an expanded end-on view of the tube stack 210(n+l) of the Figure 5.
  • two tubes 262 and 264 emanate from the inlet header 204(n+l).
  • the two tubes 262 and 264 emanate from the header 204(n+l) at each line position 260.
  • the tubes in the Figure 6 A are inclined from the inlet header 204(n) to the outlet header 206(n), which is away from the reader into the plane of the paper.
  • the tubes are in a zig-zag or staggered arrangement (as can be seen in the upper left hand of the Figure 6A), with the tube 262 traversing back and forth (in and out of the plane of the paper) in a serpentine manner between two sets of plates 250, while the tube 264 traverses back and forth (in and out of the plane of the paper) in a serpentine manner between the two sets of plates 250 in a set of holes that are in a lower row of holes from the holes through which the tube 262 travels.
  • the Figure 6A shows only one plate 250. In actuality, each tube stack may be supported by two or more sets of plates as seen previously in the Figure 4(B).
  • the tube 262 travels through holes in the odd numbered columns (1, 3, 5, 7,%) in odd numbered rows, while the tube 264 travels through even numbered columns (2, 4, 6, 8, ...) in even numbered rows.
  • This zig-zag arrangement is produced because the holes in even numbered hole columns of the metal plate are off-set from the holes in the odd numbered hole columns.
  • the tubes in one row are off set or staggered vertically from the tubes in a preceding or succeeding row.
  • the heating circuit can lie in two flow paths so as to avoid low points in the boiler and the subsequent inability to drain pressure parts.
  • FIGS 6B and 7B shown in Figures 6B and 7B below are parallel water/steam circuits 1 , 2, 3, 4, and so on.
  • FIGs 6B and 7B are inherent static head differential effects that need to be considered when designing the equipment. These static head differentials can lead to suboptimal flow and temperature distribution across the once-through section and hence a less than optimal design configuration.
  • This dynamic is termed "heat blending”. When this dynamic plays out across the entire heat exchanger it partially negates the static head effects and therefore the exact extent of heat blending is not necessarily optimal.
  • the Figure 6B is a depiction of a plane section taken within the tube stack.
  • the plane is perpendicular to the direction of travel of fluid in the tubes and the Figure 6B shows the cross-sectional areas of the 7 serpentine tubes at the plane.
  • the tubes (as viewed by their cross-sectional areas) are in a vertically staggered configuration.
  • the heating surface depicts the parallel tube paths in a staggered configuration that supports counterflow fluid flow and consequently counterflow heat transfer.
  • counterflow heat transfer it is meant that the flow in a section of a tube in one direction runs counter to the flow in another section of the same tube that is adjacent to it.
  • the numbering shown in the Figure 6B denotes a single water/steam circuit.
  • the section la contains fluid flowing away from the reader, while the section of tube lb next to it contains fluid that flows towards the reader.
  • the different tube colors in the Figure 6B indicates an opposed flow direction of the working fluid.
  • the arrows show the direction of fluid flow in a single pipe.
  • the Figure 7A depicts an isometric end-on view of tubes that are inclined in one direction while being horizontal in another direction.
  • the tubes i.e., la, lb
  • the tube stack comprises tubes that are substantially horizontal in a direction that is parallel to a direction of flow of the hot gases and inclined in a direction that is perpendicular to the direction of flow of the hot gases as shown in the Figure 8.
  • the angle ⁇ 1 can vary from 55 degrees to 88 degrees, specifically from 60 degrees to 87 degrees, and more specifically 80 degrees to 86 degrees.
  • the inclination of the tubes in one or more directions provides unoccupied space 270 between the duct wall 280 and the rectangular geometrical shape that the tube stack would have occupied if the tubes were not inclined at all.
  • This unoccupied space 270 may be used to house control equipment.
  • This unoccupied space may lie at the bottom of the stack, the top of the stack or at the top and the bottom of the stack. Alternatively, this unoccupied space can be used to facilitate counterflow of the hot gases in the tube stack.
  • this unoccupied space 270 can contain a fractional stack, i.e., a stack that is a fractional size of the regular stack 210(n) as seen in the Figures 4(A) and 4(B).
  • baffles can also be disposed in the unoccupied space to deflect the hot gases into the tube stack with an inline flow.
  • FIG 7A it may be seen that tubes are also staggered with respect to the exhaust gas flow.
  • Figure 7B depicts a plane section taken within the tube stack. The plane is generally perpendicular to the direction of travel of the working fluid in the tubes.
  • the fluid flow in the Figure 7B is also in a counterflow direction.
  • the numbering shown in the Figure 7B denotes a single water/steam circuit.
  • the arrows show the direction of fluid flow in a single tube. Since the tubes in the tube stack are inclined, the working fluid travels upwards from right to left.
  • FIGS 5, 6B, 7A, 7B show the hot gas flow from left to right, it can also flow in the opposite direction from right to left. If the hot gas flow is from right to left, the direction of flow in a single tube would be the opposite of that shown in the Figure 6B.
  • the staggered counterflow horizontally arranged heating surface ( Figure 7B) with horizontally/inclined arranged water/steam (working fluid) circuits permits a balance between increased minimum flow and increased pressure drop from a choking device. Furthermore, the heating surface is minimized due to the staggered and counterflow heat transfer mode leading to minimal draft loss and parasitic power.
  • the tubes in a tube stack are arranged in a plurality of columns and rows as may be seen in the Figure 6B.
  • the tubes of the staggered counterflow arrangement of the Figure 6B may be arranged in a plurality of columns (Col l, Col. 2, Col. 3, ...and so on).
  • the Column 1 contains tubes lb, 3b, 5b, 7b, and so on, while the Row 1 contains tubes la, lb, lc (not shown), Id (not shown) and so on.
  • a first column of tubes is separated from a neighboring second column of tubes by a distance d2.
  • the first column of tubes is separated from a third column of tubes by a distance d2 + d5.
  • the distance d2 is an average distance.
  • the distance d5 is reduced and vice versa.
  • the distance between a first tube in Column 1 and an adjacent second tube in Column 2 may vary from one pair of rows to the next depending upon design considerations.
  • the purpose of varying dl and d2 (and consequently d4 and d5) is to optimize the extent of heat blending so as to address the coincident static head differential effects present in the design in question.
  • a first row of tubes is separated from a neighboring second row of tubes by a distance dl .
  • the first row of tubes is separated from a third row of tubes disposed on the opposite side of tubes from the second row of tubes by a distance of dl + d4.
  • dl increases, d4 decreases and vice versa.
  • the location of the tube 2b determines the temperature of the exhaust gas stream that contacts it.
  • the ratio of dl to d4 determines the average temperature of the exhaust bas stream that contacts the tube 2b.
  • the distance dl is an average distance between the tubes in one row and the tubes in a neighboring row.
  • the distance between a first tube in Row 1 and an adjacent second tube in Row 2 may vary from one pair of columns to the next depending upon design considerations.
  • the tubes lb- la and 2b-2a can operate in parallel.
  • tube 2b sees exhaust flow and temperature from both tubes lb and from 3b.
  • the tubes in column 2 (Col. 2) may see a large portion of a lower temperature exhaust gas stream (than the temperature of the exhaust gas stream impinging on the tube lb and 3b) depending upon its location relative to the upstream tubes (lb and 3b) in column 1 (Col. 1).
  • the relative position of the downstream tube 2b to the upstream tubes lb and 3b determines the temperature of the blended heat stream (from tubes lb and 3b) that it (tube 2b) encounters.
  • the column of tubes located downstream of another column of tubes may see reduced temperatures.
  • the location of the tubes in the column 2 may therefore be varied in relationship to their positions with respect to the tubes in column 1 in order to adjust the amount of heat absorbed by the tubes in the column 2.
  • the same situation can occur in the Figure 7B in the case of the tubes in column 2 relative to the tubes in the column 1.
  • the relative position of the tubes in column 2 can be adjusted relative to the position of tubes in column 1 to suit a given application.
  • the distance between two adjacent tubes in the 1 st column is dl while the distance between adjacent tubes in the first column and the second column is d2.
  • a triangle contacting the tube in the first column and the second column is represented by XYZ.
  • the angle a between lines XZ and YZ may vary depending upon the lengths of dl and d2.
  • the angle a between lines XZ and YZ may vary from 2 degrees to 88 degrees and the dl can vary from 0.1 d2 to 1000d2, preferably 0.5d2 to 500d2 and more preferably d2 to 100d2. This analysis applies to the tube configuration shown in the Figure 7B as well.
  • the distance d3 between two adjacent sections 210(n) and 210(n+l) can be adjusted to increase or to decrease the amount of the incident exhaust gas stream from one section 210(n) impinging on another section 210(n+l).
  • the distance d3 can vary from dl to lOOOdl .
  • Maximum Continuous Load denotes the rated full load conditions of the power plant.
  • Approximately Horizontal Tube is a tube horizontally orientated in nature.
  • An "Inclined Tube” is a tube in neither a horizontal position or in a vertical position, but dispose at an angle therebetween relative to the inlet header and the outlet header as shown..
  • relative terms are intended to encompass different orientations of the device in addition to the orientation depicted in the Figures. For example, if the device in one of the figures is turned over, elements described as being on the “lower” side of other elements would then be oriented on “upper” sides of the other elements. The exemplary term “lower,” can therefore, encompasses both an orientation of “lower” and “upper,” depending on the particular orientation of the figure. Similarly, if the device in one of the figures is turned over, elements described as “below” or “beneath” other elements would then be oriented “above” the other elements. The exemplary terms “below” or “beneath” can, therefore, encompass both an orientation of above and below.
  • embodiments described herein should not be construed as limited to the particular shapes of regions as illustrated herein but are to include deviations in shapes that result, for example, from manufacturing.
  • a region illustrated or described as flat may, typically, have rough and/or nonlinear features.
  • sharp angles that are illustrated may be rounded.
  • the regions illustrated in the figures are schematic in nature and their shapes are not intended to illustrate the precise shape of a region and are not intended to limit the scope of the present claims.
  • the term and/or is used herein to mean both "and” as well as “or”.
  • a and/or B is construed to mean A, B or A and B.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un évaporateur à passage unique (200) comprenant une rampe d'entrée (202) ; un ou plusieurs collecteurs d'entrée (204) en communication fluidique avec la rampe d'entrée ; un ou plusieurs empilements de tubes (210), chaque empilement de tubes comprenant un ou plusieurs tubes d'évaporateur inclinés ; le ou les empilements de tubes étant en communication fluidique avec le ou les collecteurs d'entrée ; les tubes inclinés étant inclinés à un angle inférieur à 90 degrés ou supérieur à 90 degrés par rapport à la verticale ; chaque empilement de tubes comprenant une pluralité de tubes agencés dans une pluralité de colonnes et une pluralité de rangées ; une pluralité de tubes dans une première colonne étant décalés par rapport à une pluralité de tubes dans une deuxième colonne d'une distance d2, et une pluralité de tubes dans une première rangée étant décalés par rapport à une pluralité de tubes dans une deuxième rangée d'une distance d1 ; d1 variant de 0,1d2 à 1000d2 ; un ou plusieurs collecteurs de sortie en communication fluidique avec un ou plusieurs empilements de tubes ; et une rampe de sortie en communication fluidique avec le ou les collecteurs de sortie.
PCT/EP2016/065793 2015-07-09 2016-07-05 Agencement de tube dans un évaporateur horizontal à passage unique WO2017005727A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2018500533A JP2018524547A (ja) 2015-07-09 2016-07-05 貫流水平蒸発器のチューブ配置
EP16739053.3A EP3320261A1 (fr) 2015-07-09 2016-07-05 Agencement de tube dans un évaporateur horizontal à passage unique
KR1020187003894A KR20180030095A (ko) 2015-07-09 2016-07-05 관류식 수평 증발기에서의 튜브 배열
CN201680052482.2A CN107923609A (zh) 2015-07-09 2016-07-05 单程水平蒸发器中的管布置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US14/795,036 US20170010053A1 (en) 2015-07-09 2015-07-09 Tube arrangement in a once-through horizontal evaporator
US14/795,036 2015-07-09

Publications (1)

Publication Number Publication Date
WO2017005727A1 true WO2017005727A1 (fr) 2017-01-12

Family

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PCT/EP2016/065793 WO2017005727A1 (fr) 2015-07-09 2016-07-05 Agencement de tube dans un évaporateur horizontal à passage unique

Country Status (7)

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US (1) US20170010053A1 (fr)
EP (1) EP3320261A1 (fr)
JP (1) JP2018524547A (fr)
KR (1) KR20180030095A (fr)
CN (1) CN107923609A (fr)
TW (1) TW201723304A (fr)
WO (1) WO2017005727A1 (fr)

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US10317150B2 (en) * 2016-11-21 2019-06-11 United Technologies Corporation Staged high temperature heat exchanger
US10907821B2 (en) * 2019-03-07 2021-02-02 General Electric Company HRSG with stepped tube restraints
US11519597B2 (en) 2019-11-08 2022-12-06 General Electric Company Multiple cooled supports for heat exchange tubes in heat exchanger

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US20130180696A1 (en) * 2012-01-17 2013-07-18 Alstom Technology Ltd. A method and apparatus for connecting sections of a once-through horizontal evaporator

Also Published As

Publication number Publication date
US20170010053A1 (en) 2017-01-12
CN107923609A (zh) 2018-04-17
TW201723304A (zh) 2017-07-01
JP2018524547A (ja) 2018-08-30
EP3320261A1 (fr) 2018-05-16
KR20180030095A (ko) 2018-03-21

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