WO2001031278A1 - Echangeur thermique - Google Patents

Echangeur thermique Download PDF

Info

Publication number
WO2001031278A1
WO2001031278A1 PCT/US2000/029424 US0029424W WO0131278A1 WO 2001031278 A1 WO2001031278 A1 WO 2001031278A1 US 0029424 W US0029424 W US 0029424W WO 0131278 A1 WO0131278 A1 WO 0131278A1
Authority
WO
WIPO (PCT)
Prior art keywords
inlet
attached
protrusion
outlet
channel head
Prior art date
Application number
PCT/US2000/029424
Other languages
English (en)
Inventor
King Wai Chan
Original Assignee
Siemens Westinghouse Power Corporation
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 Siemens Westinghouse Power Corporation filed Critical Siemens Westinghouse Power Corporation
Publication of WO2001031278A1 publication Critical patent/WO2001031278A1/fr

Links

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
    • 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
    • F28D7/06—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 the conduits having a single U-bend
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions

Definitions

  • This invention relates generally to the field of heat exchangers, and more particularly to a heat exchanger channel head and a method of forming the channel head for a U-bend heat exchanger.
  • FIG. 1 is a schematic illustration of a U- bend heat exchanger 10 wherein only a single tube 12 is illustrated for purposes of clarity. The ends of tube 12 are aligned with and are sealingly attached to holes 14 in a tubesheet 16.
  • a channel head 18 having an inlet nozzle 20 and an outlet nozzle 22 is attached to tubesheet 16.
  • a partition 24 attached to the channel head 18 and the tubesheet 16 divides the interior of the channel head 18 into an inlet manifold 26 and an outlet manifold 28.
  • a shell 30 having an inlet nozzle 32 and an outlet nozzle 34 is attached to the tubesheet 16 on a side opposed the channel head 18.
  • a primary fluid passes into the primary side of the heat exchanger 10 through inlet nozzle 20, into inlet manifold 26, through tube 12 to outlet manifold 28, and exits the heat exchanger 10 through outlet nozzle 22.
  • a secondary fluid enters the secondary side of heat exchanger 10 through inlet nozzle 32 and exits the heat exchanger through outlet nozzle 34.
  • Heat is exchanged through the wall of the tube 12, typically from the primary (inside) of the tube 12 to the secondary (outside) of the tube 12.
  • the secondary fluid is hydrogen gas that is utilized to cool an electrical generator, and the primary fluid is water from a plant cooling water source.
  • Such applications are known as gas/water heat exchangers, wherein heat energy is transferred from the hydrogen gas on the secondary side to the cooling water on the primary side.
  • the device of this patent includes an inlet chamber as illustrated by item 126 of Figure 6 of the patent.
  • Figure 2 provides additional detail regarding the structure of a prior art hydrogen cooler such as is described in the Armstrong patent.
  • Figure 2 illustrates a tubesheet 40 having a plurality of holes 42 aligned with and sealingly attached to a plurality of tubes 44.
  • the bottom rows of tubes 46 have opposite ends that form the top rows of tubes 48.
  • the bottom rows of tubes 46 are in fluid communication with an inlet nozzle 50 and the top rows of tubes 48 are in fluid communication with an outlet nozzle 52.
  • a primary coolant such as water flows into the heat exchanger through nozzle 50, through the tube sheet 40 and into the lower rows of tubes 46, around the U-bends or through a manifold (not shown) , returning through the upper rows of tubes 48 to outlet nozzle 52.
  • a secondary side fluid such as hydrogen 54 passes across the outside surface of tubes 44 in the direction of arrow 54. It can be appreciated that as the secondary fluid 54 transfers heat into the primary side water, the temperature of the water will increase as it passes from tubes 46 to tubes 48.
  • Such an arrangement of having the secondary side fluid passing across the warmer tubes first is known in the art as a counter- flow heat exchanger.
  • the pressure drop of the secondary fluid across the heat exchanger tubes 44 should be minimized. For this reason, the number of rows of tubes in the direction of the secondary gas 54 is preferably held to a minimum value. Therefore, as the design value of the volume of flow of the secondary fluid 54 is increased, the depth D of the heat exchanger, as shown in Figure 2, is preferably maintained at an optimal value while the width is increased. Second, the flow rate of fluid through the tubes should be maintained below a predetermined value to reduce pressure loss and erosion. For a typical design, the total cross sectional area of the tubes 44 is approximately equal to the cross sectional area of the nozzles 50, 52.
  • the velocity of the fluid through the tubes 44 is approximately equal to the velocity of the fluid through the inlet nozzle 50 or outlet nozzle 52. It may be appreciated, therefore, that as the design flow rate of the secondary fluid is increased, and the width W of the heat exchanger is increased, the number of tubes 44 in a given row of tubes will increase, as will the diameter of the inlet nozzle 50 and outlet nozzle 52. Beyond a certain design size, the diameter of the nozzles 50, 52 will each be greater than ⁇ the depth D of the tube sheet 40. When this occurs, the design of the channel head connecting the nozzles 50, 52 to the tubesheet 40 becomes complicated, since a simple manifold having a circular opening opposed the tube sheet is not possible.
  • Figure 2 illustrates a chamber 56 having a partition 58 that divides the tubesheet 40 into an inlet manifold 60 and an outlet manifold 62. Because the depth d of the inlet manifold 60 and outlet manifold 62 are each less than the respective diameters of nozzles 50, 52, a cover 64 is provided having a diagonal partition 66 along its top half for providing a connection to nozzles 50, 52. Within the bottom half of cover 64 (nearest chamber 56) flow passages (not shown) are formed to direct the flow from the respective nozzle 50, 52 to the appropriate manifold 60, 62. These flow passages are complicated to manufacture and increase the pressure drop of the primary fluid across the cover 64.
  • nozzles 50, 52 are necessarily placed at the respective far ends of the cover 64 where there is sufficient space defined by the diagonal partition 66. Such an arrangement is not optimal for distributing the flow of the primary fluid evenly across the width W of the tube sheet 40. What is needed, therefore, is an improved heat exchanger design that provides a more even distribution of the primary fluid across the width of the tube sheet, and that is more economical to manufacture for applications requiring a relatively large volume of secondary fluid flow with a minimum of secondary fluid pressure loss.
  • a channel head for a heat exchanger having: a wall member having four sides connected in a generally rectangular shape and having a first surface formed to be attached to a tube sheet; a cover attached to the wall member along a second surface opposed the first surface, the cover comprising an inlet nozzle and an outlet nozzle; a partition attached to the cover between the inlet nozzle and the outlet nozzle along an edge of the partition and attached to opposed sides of the wall member to form an inlet manifold and an outlet manifold; and, wherein the edge of the partition comprises protrusions formed to circumvent portions of the inlet and outlet nozzles respectively.
  • Figure 1 is a schematic representation of a prior art U-bend heat exchanger.
  • Figure 2 illustrates the tubesheet and channel head design of a prior art heat exchanger utilized as a hydrogen cooler for an electrical generator.
  • Figure 3 illustrates the channel head of a heat exchanger having protrusions formed from sections of a pipe elbow.
  • Figure 4 illustrates the locations of cuts made in a pipe elbow to form the protrusions for a heat exchanger channel head.
  • Figure 5 illustrates the channel head of a heat exchanger having protrusions formed from welded members.
  • FIG. 3 illustrates the channel head 70 of a heat exchanger built in accordance with the present invention. It may be appreciated that channel head 70 may be utilized in place of the chamber 56, cover 64, and inlet and outlet nozzles 50, 52 of a prior art heat exchanger as is illustrated in Figure 2.
  • Channel head 70 includes a wall member 72 having four sides connected in a generally rectangular shape. Wall member 72 functions as a pressure boundary for the primary fluid.
  • Wall member 72 includes a flat surface 74 formed for attachment to a tube sheet, such as tube sheet 40 of Figure 2.
  • Surface 74 may typically be a flat surface containing a plurality of holes 76 through which bolts or other connectors (not shown) are passed for connection with the tubesheet (not shown) .
  • a cover 78 is attached to the wall member 72 along a second surface opposed the first surface 74.
  • the cover 78 also functions as a portion of the pressure boundary for the primary fluid, and it includes opening for inlet nozzle 80 and outlet nozzle 82 connections.
  • a partition 84 is attached to the cover 78 and to opposed sides of wall member 72 to divide the interior volume of the wall member 72 into an inlet manifold 86 and an outlet manifold 88.
  • Partition 84 includes a generally planer plate portion 90 having an edge 92 formed to be attached to the tubesheet along a line between the inlet tubes (such as rows of tubes 46 on Figure 2) and outlet tubes (such as rows of tubes 48 on Figure 2) .
  • Partition 84 serves as a boundary between the inlet and outlet sides of the channel head 70 on the primary side of the heat exchanger .
  • Partition 84 also includes an inlet protrusion 94 and an outlet protrusion 96.
  • Protrusions 94, 96 are formed to circumvent those portions of the inlet nozzle 80 and outlet nozzle 82 respectively that extend beyond the projection of a center line defined by the planer portion 90 of the partition 84.
  • Protrusions 94, 96 serve to direct the water from the respective nozzles 80, 82 into the appropriate manifolds 86, 88, thereby allowing the diameter of the openings for nozzles 80, 82 to be greater than the depth d of the inlet and outlet manifolds 86, 88.
  • protrusions 94, 96 allows the design of the heat exchanger to have a generally thin depth D so that the pressure loss of the secondary fluid as it passes over the rows of tubes is minimized, while at the same time allowing the width W to be extended to include more tubes so that the volume of both the primary and secondary fluid flows can be increased.
  • the corresponding increase in the diameters of nozzles 80, 82 can be accommodated by incorporating protrusions 94, 96 into the structure of the partition 84, thereby eliminating the need for the separate chamber 56 and cover 64 of the prior art.
  • Protrusions 94, 96 may be formed by separating a standard pipe elbow into two sections.
  • Figure 4 illustrates a standard short radius pipe elbow 100 that may be used to form protrusions 94, 96.
  • Pipe elbow 100 may be separated into two sections by cutting along line 102 with any process known in the art for metal cutting, thereby forming a protrusion 104.
  • pipe elbow 100 may be separated along line 106 for a channel head requiring a larger protrusion.
  • a single pipe elbow may be cut to form two protrusions from the single pipe elbow.
  • the channel head 70 of Figure 3 may be formed from any material known in the art, for example carbon or stainless steel casting, forging or plate.
  • the wall member 72, partition 84, and protrusions 94, 96 may be formed from a plurality of pieces of material that are joined in any manner known in the art, such as by welding. Alternatively, these pieces may be formed from a single piece of material, with the appropriate void areas machined or otherwise removed therefrom.
  • Channel head 70 may be formed by first machining a channel head surface 74 onto raw material .
  • the surface 74 is adapted to be attached to the tubesheet of a U-bend heat exchanger.
  • the inlet manifold 86 and outlet manifold may then be formed by additional machining from the surface 74.
  • Material remaining after such a machining operation defines the inside surfaces of wall member 72, the interior surface of cover 78, the planer portion of partition 84, and the upper surface of protrusions 94, 96.
  • a cover surface may then be machined onto the material on a side opposed surface 74, and openings connecting with the inlet and outlet manifolds 86,88 then formed in that surface for the inlet nozzle 80 and outlet nozzle 82. Additional material may then be removed to form the inside surface 97 of protrusion 96 and the respective surface (not shown) for protrusion 94.
  • Holes 76 may be drilled into wall member 72 from either side of the material. Inlet nozzle 80 and outlet nozzle 82 may then be attached, such as by welding, to the openings formed in the cover 78.
  • the wall member 72 may be formed by welding together four separate pieces of material. Cover 78 is then attached to the wall member 72.
  • Partition 84 may be formed by joining a planer section 90 to opposed sides of wall member 72, separating a pipe elbow into two sections to form protrusions 94, 96, and then attaching the protrusions 94, 96 to the planer section 90 and to the cover 78 along a line circumventing the openings for inlet nozzle 80 and outlet nozzle 82, respectively.
  • Holes 76 are drilled into the wall member 72 and the channel head 70 may then be attached to the tube sheet of a heat exchanger, such as the tube sheet 70 of Figure 2.
  • FIG. 5 is a perspective view of a channel head 110 which is similar to the channel head 70 of Figure 3 but having an alternative embodiment of the protrusions.
  • the protrusions 112, 114 are fabricated by joining together a plurality of separate members.
  • Each protrusion 112, 114 contains two opposed planar members 116 joined by a curvilinear member 118.
  • the opposed planar members 116 are attached, such as by welding, to the planar section 90, to the curvilinear member 118, and to the cover 78.
  • the curvilinear members 118 are attached to the respective opposed planar members 116, to the planar section 90 and to the cover 78.
  • protrusions 112,114 take a scoop shape encompassing the respective inlet nozzle 80 or outlet nozzle 82.
  • the width W of channel head 70 may be increased to accommodate wider rows of tubes in the heat exchanger.
  • the location of inlet nozzle 80 and outlet nozzle 82 is preferably maintained proximate the center of the width W of the channel head 70. This will ensure that the distribution of flow across the channel head face is as symmetric as possible.
  • the diameter of the openings formed for the inlet nozzle 80 and outlet nozzle 82 may be increased to a value that is greater than the width d of the inlet and outlet manifolds 86, 88.
  • the protrusions 94, 96 serve to direct this flow to and from the respective nozzles into the appropriate manifolds 86, 88.
  • manifolds 86, 88 define respective rectangular shaped areas that correspond to the inlet and outlet portions of the tube sheet.
  • the manifolds 86, 88 define a generally rectangular shaped area interrupted by one of the protrusions 94, 96 respectively.
  • Planer section 90 of partition 84 is formed with a top edge 92 that defines the division between the inlet and outlet sections of the tube sheet.
  • Partition 84 also includes a bottom edge 93 that is attached to cover 78, with the edge 93 including respective edges of protrusions 94, 96 formed to circumvent portions of the inlet nozzle 80 and outlet nozzle 82 respectively.
  • protrusions 94, 96 eliminate the need for a separate chamber 56 and cover 64 as is shown in the prior art heat exchanger of Figure 2.
  • the pressure loss through manifold 70 will be less than the pressure drop through a corresponding manifold built in accordance with the prior art design of Figure 2.
  • inlet nozzle 80 and outlet nozzle 82 can be maintained proximate a center of the width W of the tube sheet, the flow distribution provided by channel head 70 is improved when compared to the prior art design of Figure 2. Lastly, because of the simplified structure and reduction in number of parts and/or manufacturing steps, the manifold 70 is less expensive to manufacture than the prior art design.

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  • 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 une prise (70) d'eau pour échangeur thermique caractérisée en ce que les diamètres de la buse d'entrée (80) et de la buse de sortie (82) sont plus importants que les profondeurs respectives du collecteur d'entrée (86) et du collecteur de sortie (88). Des protubérances (94, 96) constituent une partie de la séparation (84) entre le collecteur d'entrée (86) et le collecteur de sortie (88) servant à diriger le flux d'un fluide primaire des buses surdimensionnées aux parties correspondantes de la plaque tubulaire (40). Lesdites protubérances (94, 96) peuvent être formées par le découpage en segments d'un coude de tuyau.
PCT/US2000/029424 1999-10-28 2000-10-25 Echangeur thermique WO2001031278A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US42909799A 1999-10-28 1999-10-28
US09/429,097 1999-10-28

Publications (1)

Publication Number Publication Date
WO2001031278A1 true WO2001031278A1 (fr) 2001-05-03

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ID=23701789

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2000/029424 WO2001031278A1 (fr) 1999-10-28 2000-10-25 Echangeur thermique

Country Status (1)

Country Link
WO (1) WO2001031278A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2253999A1 (es) * 2003-08-07 2006-06-01 Framatome Anp. Intercambiador de calor y, en particular, generador de vapor con fondo convexo.
WO2009156055A1 (fr) * 2008-06-26 2009-12-30 Behr Gmbh & Co. Kg Échangeur de chaleur pour véhicule automobile
US20150285570A1 (en) * 2012-10-10 2015-10-08 Jon Phillip Hartfield Water head for an evaporator
WO2017144989A3 (fr) * 2016-01-29 2017-10-05 Sperre Coolers As Système modulaire pour échangeurs de chaleur

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4396060A (en) * 1981-07-10 1983-08-02 Artur Schenk Pipe manifold for central heating systems
US4520867A (en) * 1984-02-06 1985-06-04 General Motors Corporation Single inlet/outlet-tank U-shaped tube heat exchanger
US5265673A (en) * 1993-03-02 1993-11-30 Aos Holding Company Compact manifold for a heat exchanger with multiple identical heating tubes
JPH08240395A (ja) * 1995-03-06 1996-09-17 Zexel Corp 熱交換器
DE19942458A1 (de) * 1998-09-29 2000-03-30 Denso Corp Wärmetauscher für eine Fahrzeug-Klimaanlage
DE19857382A1 (de) * 1998-12-12 2000-06-15 Behr Gmbh & Co Wärmeübertrager, insbesondere für Kraftfahrzeuge

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4396060A (en) * 1981-07-10 1983-08-02 Artur Schenk Pipe manifold for central heating systems
US4520867A (en) * 1984-02-06 1985-06-04 General Motors Corporation Single inlet/outlet-tank U-shaped tube heat exchanger
US5265673A (en) * 1993-03-02 1993-11-30 Aos Holding Company Compact manifold for a heat exchanger with multiple identical heating tubes
JPH08240395A (ja) * 1995-03-06 1996-09-17 Zexel Corp 熱交換器
DE19942458A1 (de) * 1998-09-29 2000-03-30 Denso Corp Wärmetauscher für eine Fahrzeug-Klimaanlage
DE19857382A1 (de) * 1998-12-12 2000-06-15 Behr Gmbh & Co Wärmeübertrager, insbesondere für Kraftfahrzeuge

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 01 31 January 1997 (1997-01-31) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2253999A1 (es) * 2003-08-07 2006-06-01 Framatome Anp. Intercambiador de calor y, en particular, generador de vapor con fondo convexo.
WO2009156055A1 (fr) * 2008-06-26 2009-12-30 Behr Gmbh & Co. Kg Échangeur de chaleur pour véhicule automobile
DE102008029958A1 (de) * 2008-06-26 2009-12-31 Behr Gmbh & Co. Kg Wärmetauscher für ein Kraftfahrzeug
CN102066868A (zh) * 2008-06-26 2011-05-18 贝洱两合公司 用于机动车的换热器
US20150285570A1 (en) * 2012-10-10 2015-10-08 Jon Phillip Hartfield Water head for an evaporator
US10697717B2 (en) * 2012-10-10 2020-06-30 Trane International Inc. Water head for an evaporator
WO2017144989A3 (fr) * 2016-01-29 2017-10-05 Sperre Coolers As Système modulaire pour échangeurs de chaleur

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