[go: up one dir, main page]

WO2002029349A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur

Info

Publication number
WO2002029349A1
WO2002029349A1 PCT/US2001/042443 US0142443W WO0229349A1 WO 2002029349 A1 WO2002029349 A1 WO 2002029349A1 US 0142443 W US0142443 W US 0142443W WO 0229349 A1 WO0229349 A1 WO 0229349A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
shell
tubes
fluid
heat exchanger
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.)
Ceased
Application number
PCT/US2001/042443
Other languages
English (en)
Inventor
Joseph Kaellis
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.)
Individual
Original Assignee
Individual
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
Priority claimed from US09/680,387 external-priority patent/US6808017B1/en
Application filed by Individual filed Critical Individual
Priority to AU2001296969A priority Critical patent/AU2001296969A1/en
Publication of WO2002029349A1 publication Critical patent/WO2002029349A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0132—Auxiliary supports for elements for tubes or tube-assemblies formed by slats, tie-rods, articulated or expandable rods
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • This invention relates generally to shell and tube heat exchangers, and, more specifically to mini-vortex generators and sinuous baffles used in shell and tube-type heat exchangers.
  • Heat transfer is an important engineering concern for many process.
  • Heat exchangers are a well known apparatus for transferring heat from one medium to another.
  • There are many types of heat exchangers including for example shell and tube designs, double pipe type shell and tube designs, plate and frame designs, plate-fin designs, and others. These heat exchangers are used in many industries, including those engaged in generating energy, producing chemicals, refining petroleum products, and air conditioning. All of these industries would stand to benefit from a more efficient heat exchanger design.
  • a common goal in the design of shell and tube-type heat exchangers is to enhance heat transfer while trying to keep the associated pressure drop low, or in other words to maximize the ratio of the heat transfer coefficient to the pressure drop.
  • a problem with existing shell and tube type heat exchanger designs is a failure to maximize the heat transfer coefficient while keeping the pressure drop to a minimum. This is evidenced in shell and tube exchangers utilizing segment type baffles, which generate flow perpendicular to the tube bundle, which is otherwise known as crossflow. These baffles have a high heat transfer coefficient but also have a high pressure drop resulting from the crossflow.
  • current commercial designs utilizing grid baffles with flow parallel to the tube bundle have a low pressure drop but have a less favorable heat transfer coefficient. Consequently the overall efficiency, as measure by the ratio of the heat transfer coefficient to pressure drop, is not maximized in current shell and tube type heat exchangers. What is needed is a shell and tube type heat exchanger that improves upon the heat transfer coefficient to pressure drop ratio of current shell and tube heat exchangers utilizing grid type baffles.
  • the invention satisfies this need.
  • the invention is a shell and tube type heat exchanger that provides a greater heat transfer coefficient to pressure drop ratio and is thus more efficient.
  • the heat exchanger has a shell and a tube bundle inside the shell.
  • the tube bundle includes a plurality of substantially parallel tubes for passage of a first fluid. At least a portion of the tubes have a mini- vortex generator on their exterior surface.
  • the heat exchanger further includes a grid baffle between the tubes, a tube inlet for passage of the first fluid into the tubes, and a tube outlet for passage of the first fluid out of the tube.
  • the shell has a shell outlet for passage of a second fluid into the shell and exterior to the tubes and a shell outlet for withdrawing a second fluid from the shell.
  • the heat exchanger has a shell and a tube bundle inside the shell.
  • the tube bundle includes a plurality of substantially parallel tubes for passage of a first fluid.
  • the heat exchanger has sinuous baffles for supporting the tubes.
  • Each sinuous baffle includes a plurality of wiggle bar tube support members disposed between the tubes.
  • the heat exchanger further includes a tube inlet for passage of the first fluid into the tubes and a tube outlet for passage of the first fluid out of the tube.
  • the shell has a shell outlet for passage of a second fluid into the shell and exterior to the tubes and a shell outlet for withdrawing the second fluid from the shell.
  • the heat exchanger has sinuous baffles and at least a portion of the tubes of the heat exchanger have a mini-vortex generator on their exterior surface.
  • Figure 1 is a cross-sectional side view of a heat exchanger having features of the invention
  • FIG. 2 is a perspective view of a heat exchanger tube, including an enlarged scale view of a mini- vortex generator having features of the invention
  • Figure 3 is a side elevation in partial coss-section of the heat exchanger illustrated in
  • Figure 4 is a coss-sectional view of the heat exchanger illustrated in Figure 1 , taken along line 4-4;
  • Figure 5 is a coss-sectional view of the heat exchanger illustrated in Figure 1, taken along line 5-5;
  • Figure 6 is a coss-sectional view of the heat exchanger illustrated in Figure 1, taken along line 6-6.
  • the invention is a heat exchanger 10 having a shell 12, a tube bundle 14 having a plurality of tubes 16 within the shell 12, and a grid baffle 18 between the tubes 16.
  • the shell 12 encloses the tube bundle 14 and holds the shell fluid 20 as it passes against the exterior of the tubes 16.
  • the shell 12 typically has two outlets, a first shell outlet 22 for passage of the shell fluid 20 (otherwise referred to herein as the second fluid) into the shell 12 and a second shell outlet 24 for withdrawing the shell fluid 20 from the shell 12 and out of the heat exchanger 10.
  • the outlets are typically configured as nozzles.
  • the shell 12 is typically a pipe, rolled cylinder, or similar such cylindrical tank-like structure.
  • the diameter of the shell 12 is typically between about 20 cm (8") and about 77 cm (30"), or other sizes as needed. More typically, the diameter of the shell 12 is between about 30 cm (12") and about 64 cm (25").
  • the length of the shell 12 is typically between about 3 m (10 feet) and about 14 m (45 feet).
  • the tube bundle 14 comprises two tube sheets 26 that are affixed to the shell 12.
  • the tube sheets 26 separate the tube fluid 28 (otherwise referred to herein as the first fluid 28) from the shell fluid 20 and support the end portions of the tubes 16 within the shell 12.
  • the tube sheets 26 have tube holes 30 through which the tubes 16 protrude.
  • the tubes 16 are typically welded directly to the tube hole 30 of the tube sheet 26, or expanded by rolling to give a leak-proof fit.
  • the tube sheet 26 is typically a metal such as steel, aluminum, admiralty metal, or others.
  • one tube sheet 26 is affixed to the shell 12 and the other tube sheet 26 is floating and is not affixed to the shell 12. This design permits the tubes bundle 14 to be removable.
  • the tube bundle 14 comprises one tube sheet 26 with U-tubes.
  • the tube bundle 14 is comprised of a plurality of tubes 16 that are disposed substantially parallel to each other and parallel to the longitudinal axis of shell 12.
  • the heat exchanger 10 has a tube inlet 32 for passage of tube fluid 28 through a first header 33a into the tubes 16 and a tube outlet 34 for passage of the tube fluid 28 from the tubes 16 into a second header 33b and out of the heat exchanger 10.
  • the tube inlet 32 and the tube outlet 34 are disposed on opposite ends of the heat exchanger 10.
  • the tube inlet 32 and tube outlet 34 are disposed at the same end of the heat exchanger 10.
  • the tubes 16 are typically formed of a metal, such as steel, copper, aluminum, or admiralty metal.
  • the diameter of the tubes 16 is typically between about 1 cm (Vz") and about 5 cm (2"). More typically, the diameter of the tubes 16 is between about 1.5 cm (5/8") and 2.5 cm (1").
  • the tubes 16 have a mini- vortex generator 36 on their exterior surface.
  • the function of the mini- vortex generator 36 is to abruptly interrupt the flow of the shell fluid 20 proximal to the exterior surface of the tube 16.
  • the mini-vortex generators 36 comprise small protrusions on the external surface of the tubes 16 which interrupt the longitudinal flow of the shell fluid 20 proximal to the tubes 16 exterior surface. This interruption in fluid flow by the mini- vortex generators 36 results in a shell fluid 20 flow which can be described as recirculating, separated, or a vortex flow.
  • the result is a disruption of the shell fluid 20 laminar sub-layer which exist in turbulent flow conditions and is proximal to the tube 16, and a corresponding disruption in the temperature profile close to the tube 16 wall.
  • the vortex fluid flow process results in a decrease in resistance close to the exterior of the tube 16 wall and an increase in the heat transfer rate.
  • the heat transfer benefit of the invention is generally greatest for fluids having a high or moderate Prandtl number where heat transfer occurs to a large extent by a movement of the fluid mass which contains the heat, as opposed to heat transfer in fluids with a low Prandtl number where heat is transferred predominantly by conduction.
  • the mini-vortex generators 36 are comprised of ridge members 36a that encircle at least a portion of the exterior surface of the tubes 16.
  • the ridge members 36a are integral with the tubes 16.
  • the ridge members 36a have a flow blocking surface 38 that disrupts the longitudinal flow of the shell fluid 20 proximal to the exterior surface of the tubes 16.
  • the ridge members 36a are disposed generally perpendicular to the longitudinal axis of the tubes 16, and each ridge member 36a disrupts the shell fluid 20 flow predominantly upstream of itself.
  • the ridge members 36a are configured as annular rings 36a that protrude from the external surface of the tubes 16.
  • the ridge members 36a have a sloped surface 40 that is disposed rearward of the flow blocking surface 38 such that the fluid vortex is created upstream of the flow blocking surface 38 and the surrounding shell fluid 20 passes by the slopped surface 40 after it encounters the flow blocking surface 38.
  • the ridge member 36a has an alternative configuration in cross-section such as for example square, rectangular, beveled rectangular, or curved.
  • the mini- vortex generator 36 comprises spiral-like ridges 36b that wind around the exterior surface of the tubes 16.
  • the mini- vortex generator 36 comprises alternative protrusions or alterations on the exterior surface of the tubes 16.
  • the height of the ridge member 36a from the exterior tube 16 surface is between about 0.2 mm and about 1.0 mm on a tube 16 having a base diameter of between about 1.5 cm (5/8") and about 2.5 cm (1").
  • the diameter of the portion of the tube 16 having a ridge member 36a is preferably greater than the base diameter by about 0.4 mm to about 2.0 mm.
  • the height of the ridge members 36a is greater.
  • a heat exchanger 10 using a shell fluid 20 that is high fouling or which tends to form deposits on the tubes 16 should utilize ridge members 36a of between about 1 mm and about 3 mm to offset deposit formation on the tubes 16 caused by the shell fluid 20.
  • the height of the ridge members 36a is greater than 3 mm.
  • the spacing between ridge members 36a otherwise known as the pitch, is between about 2 mm and about 15 mm.
  • the pitch of the ridge members 36a is between about 2.6 mm and about 13 mm.
  • the pitch is between about 2 mm and about 40 mm.
  • the pitch of the ridge members 36a increases in relation to their height.
  • the pitch of the ridge members 36a is between about 10 times and about 15 times the height of the ridge members 36a.
  • the height of the ridge members 36a is selected to minimize the pressure drop of the shell fluid 20 while maximizing heat transfer.
  • the width of each ridge member 36a is typically between about 0.2 mm and about 1.0 mm, and is variable when one or more surface of the ridge member 36a is sloped, beveled, curved, or otherwise non-rectangular in cross-section.
  • Baffles in a heat exchanger 10 function to support the tubes 16 and to direct the flow of the shell fluid 20.
  • the term grid baffle 18 as use herein refers to a baffle that permits longitudinal shell fluid 20 flow (parallel to the longitudinal axis of the shell 12).
  • heat exchangers 10 utilizing segmented baffles generate a shell fluid 20 crossflow (perpendicular to the tube bundle 14) as opposed to a longitudinal flow (parallel to the tube bundle 14).
  • Each grid baffle 18 comprises a plurality of tube support members 42.
  • each tube support member 42 is elongate and spans at least a portion of the shell 12 in a plane perpendicular to the longitudinal axis of the shell 12.
  • each tube support member 42 has opposed ends that are attached to a baffle hoop 44 that is disposed within the shell 12 in a plane substantially perpendicular to the tube bundle 14.
  • the spacing of grid baffles 18 within the shell 12 depend on the tube 16 diameter.
  • Tubes 16 having a 2.5 cm (1") diameter are typically supported every 150 cm (60") along the tubes 16 longitudinal axis
  • tubes 16 having a 2 cm (3/4") diameter are typically supported every 115 cm (45")
  • tubes 16 having a 1 cm (V2”) diameter are typically supported every 76 cm (30").
  • each grid baffle 18 may furnish only partial support for the tube 16, the baffle spacing generally does not exceed an integer fraction of 150 cm (60"), 115 cm (45"), or 76 cm (30").
  • the heat exchanger 10 comprises sinuous baffles 18a (referred to as slat baffles in related application No. 60/157,880), which are a type of grid baffle 18.
  • each sinuous baffle 18a has a plurality of tube support members 42 which are referred to herein as wiggle bars 42a.
  • the wiggle bars 42a have a sinusoidal or wave-like configuration about a elongate axis that spans the baffle hoop 44, and the wiggle bars 42a are disposed between the tubes 16 to provide support for the tubes 16.
  • a tube 16 can also be supported directly by the baffle hoop 44 on one side to maximize the tube 16 packing.
  • the heat exchanger 10 comprises groups of three sinuous baffles 18a whereby the elongated axis of the wiggle bars 42a of each sinuous baffle 18a are oriented at 60° relative to the nearest sinuous baffle.
  • the tubes 16 are supported by a sinuous type baffle every 50 cm (20") or less (150 divided by the integer 3) and each baffle is rotationally disposed 60° relative to the nearest sinuous baffle.
  • Tube support members 42 in a grid baffle 18 produce resistance to the longitudinal flow of the shell fluid 20.
  • this series of three sinuous baffles 18a allows maximal flow area at each sinuous baffle 18a, thus minimizing the resistance to the longitudinal flow of the shell fluid 20 while still providing tube 16 support.
  • the depth (dimension parallel to the longitudinal tube axis) of the wiggle bar 42a is between about 0.6 cm (1/4") and about 1 cm (1/2").
  • the spacing between tube centers, otherwise known as the tube pitch, is typically 1-1/4 times the tube diameter as required by TEMA.
  • the width of the wiggle bar 42a, the distance between the exterior surface of two adjacent tubes 16, is thus typically 1/4 times the tube 16 diameter.
  • the width of a wiggle bar 42a for a heat exchanger 10 utilizing tubes 16 with 2 cm (3/4") diameter is typically about 0.5 cm (3/16").
  • the width of a wiggle bar 42a for a heat exchanger 10 utilizing tubes 16 with a 2.5 cm (1") diameter is typically about 0.6 cm (1/4").
  • the tube 16 pitch and wiggle bar 42a width may vary in alternative embodiments.
  • the width of the wiggle bars 42a may be slightly less than 1/4 times the tube 16 diameter in order to allow clearance for the mini- vortex generators 36.
  • Pitch to diameter ratios larger than required by TEMA give a less compact tube packing density.
  • the advantage of sinuous baffles 18a is that they allow the tubes 16 to be oriented with a triangular pitch. A triangular pitch, as opposed to a square pitch permits a greater tube 16 packing density with about 15-1/2% more tubes in the same diameter tube bundle 14.
  • the heat exchanger 10 typically further comprises one or more blocking bars integral with or attached to the baffles 18 at the pass section of the shell 12 to prevent shell fluid 20 bypass.
  • Tube bundles 14 are, preferably packed as fully as possible with tubes 16 to eliminate large fluid passageways on the periphery of the tube bundle 14 which permit shell fluid 20 to bypass the tube bundle 14. Passageways which still remain are preferably blocked by attaching nodules or protrusions on the baffle hoop 44.
  • each tube 16 is in contact and is supported by two wiggle bars 42a, with the exception of some tubes 16 disposed proximal to the baffle hoop 44.
  • each wiggle bar 42a is in contact with a portion of the circumference of external surface of each tube 16 defined by an arc (corresponding to an angle of a portion of the circular tube 16) of between about 30° and about 180° .
  • each wiggle bar 42a is in contact with a portion of the circumference of each tube 16 defined by an arc (corresponding to an angle of a portion of the circular tube 16) of between about 45° and about 75°.
  • a tube 16 contacts one wiggle bar 42a on one side of the tube 16 along about a 60° arc and the same tube 16 contacts another wiggle bar 42a along about a 60° arc on the opposing side of the tube 16. Accordingly, for each sinuous baffle 18a most tubes 16 are in supporting contact with a wiggle bar 42a over a total arc circumference corresponding to a combined angle of about 120°.
  • the second sinuous baffle 18a in a series contacts the same tube 16 at two opposing arcs rotationally displaced about 60° from the first sinuous baffle, and the third sinuous baffle 18a in series contacts the same tube at two opposing arcs rotationally displaced about 60° from the second sinuous baffle.
  • the tube 16 has been contacted three times at three adjacent sections of the tube 16 circumference, each contact being 120°, or a total of 360°, with depth of the contact surface being equivalent to the depth of the wiggle bar 42a.
  • the tube 16 has now been contacted, and is supported around its entire periphery.
  • the next sinuous baffle 18a begins a new series of three.
  • the invention further includes a method of heat exchange between fluids comprising utilizing the heat exchanger 10 described herein.
  • the first and second fluid are passed either countercurrent, co-current, or in multi-pass with substantially parallel flow.
  • the first and second fluid are passed in substantially counter-current directions (in opposite directions) or in multi-pass flow, and parallel to the longitudinal axis of shell 12. A transfer of heat occurs between the fluids when the first fluid and second fluid are at different temperatures.

Landscapes

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

Abstract

L'invention concerne un échangeur de chaleur à calandre (10) caractérisé par un rapport coefficient de transfert de chaleur/chute de pression plus important. L'invention comprend un générateur de mini-vortex (36) placé sur la surface des tubes (16) du faisceau de tubes (14) dans la calandre (12) de l'échangeur de chaleur (10). Le générateur de mini-vortex (36) augmente le coefficient de transfert de chaleur dans les échangeurs de chaleur de type à chicane à grille présentant un écoulement de fluide à calandre longitudinal, sans provoquer d'augmentation importante de la chute de pression. L'invention concerne également une chicane à grille alambiquée (18a) qui garantit une meilleure densité de garnissage de tubes et une moindre chute de pression dans un échangeur de chaleur à écoulement de fluide de calandre longitudinal. Par ailleurs, l'invention concerne un échangeur de chaleur à calandre (10) comportant des générateurs de mini-vortex (36) et des chicanes alambiquées (18a).
PCT/US2001/042443 2000-10-04 2001-10-01 Echangeur de chaleur Ceased WO2002029349A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001296969A AU2001296969A1 (en) 2000-10-04 2001-10-01 Heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US09/680,387 2000-10-04
US09/680,387 US6808017B1 (en) 1999-10-05 2000-10-04 Heat exchanger

Publications (1)

Publication Number Publication Date
WO2002029349A1 true WO2002029349A1 (fr) 2002-04-11

Family

ID=24730891

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2001/042443 Ceased WO2002029349A1 (fr) 2000-10-04 2001-10-01 Echangeur de chaleur

Country Status (2)

Country Link
AU (1) AU2001296969A1 (fr)
WO (1) WO2002029349A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104142088A (zh) * 2014-08-01 2014-11-12 张家港化工机械股份有限公司 特种换热器中管束的支撑架
CN106943805A (zh) * 2017-04-26 2017-07-14 哈尔滨汽轮机厂辅机工程有限公司 一种汽水分离再热装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3326282A (en) * 1965-02-08 1967-06-20 Rosenblads Patenter Ab Arrangement for fastening spiral wire spacers in tubular heat exchangers
US3720259A (en) * 1969-09-26 1973-03-13 Waagner Biro Ag Tubular heat exchanger supporting and spacer structure
US3837397A (en) * 1971-03-19 1974-09-24 Ca Atomic Energy Ltd Tube bundle assembly
US4204570A (en) * 1978-02-23 1980-05-27 Foster Wheeler Energy Corporation Helical spacer for heat exchanger tube bundle
US4588027A (en) * 1982-02-12 1986-05-13 Phillips Petroleum Company Finned or serrated rod baffles for finned tube-shell heat exchanger
US4809415A (en) * 1982-11-02 1989-03-07 Tokyo Shibaura Denki Kabushiki Kaisha Method of manufacturing a heat exchange pipe
US5181560A (en) * 1990-10-17 1993-01-26 Burn Mark N Baffleless tube and shell heat exchanger having fluted tubes
US5255737A (en) * 1990-07-09 1993-10-26 Phillips Petroleum Company Heat exchanger with flow distribution means

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3326282A (en) * 1965-02-08 1967-06-20 Rosenblads Patenter Ab Arrangement for fastening spiral wire spacers in tubular heat exchangers
US3720259A (en) * 1969-09-26 1973-03-13 Waagner Biro Ag Tubular heat exchanger supporting and spacer structure
US3837397A (en) * 1971-03-19 1974-09-24 Ca Atomic Energy Ltd Tube bundle assembly
US4204570A (en) * 1978-02-23 1980-05-27 Foster Wheeler Energy Corporation Helical spacer for heat exchanger tube bundle
US4588027A (en) * 1982-02-12 1986-05-13 Phillips Petroleum Company Finned or serrated rod baffles for finned tube-shell heat exchanger
US4809415A (en) * 1982-11-02 1989-03-07 Tokyo Shibaura Denki Kabushiki Kaisha Method of manufacturing a heat exchange pipe
US5255737A (en) * 1990-07-09 1993-10-26 Phillips Petroleum Company Heat exchanger with flow distribution means
US5181560A (en) * 1990-10-17 1993-01-26 Burn Mark N Baffleless tube and shell heat exchanger having fluted tubes

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104142088A (zh) * 2014-08-01 2014-11-12 张家港化工机械股份有限公司 特种换热器中管束的支撑架
CN106943805A (zh) * 2017-04-26 2017-07-14 哈尔滨汽轮机厂辅机工程有限公司 一种汽水分离再热装置

Also Published As

Publication number Publication date
AU2001296969A1 (en) 2002-04-15

Similar Documents

Publication Publication Date Title
US6808017B1 (en) Heat exchanger
EP0443340B1 (fr) Echangeur de chaleur
US4204570A (en) Helical spacer for heat exchanger tube bundle
EP2469215B1 (fr) Echangeur de chaleur à tube
CN101551207B (zh) 管壳式螺旋扁管换热器
JP4268818B2 (ja) 熱交換器の流通チューブ支持体
US4398595A (en) Vortex generators
US4311187A (en) Vortex generators
US20040069470A1 (en) Bent-tube heat exchanger
US5472047A (en) Mixed finned tube and bare tube heat exchanger tube bundle
CN2672595Y (zh) 一种倾斜折流板列管式换热器
CN110057214A (zh) 一种换热装置
WO2011115748A1 (fr) Plateaux de contact fendus pour échangeurs de chaleur
CN1140764C (zh) 缩放管全逆流双壳程轴流式换热器及其换热方法
US5255737A (en) Heat exchanger with flow distribution means
WO2002029349A1 (fr) Echangeur de chaleur
CN207147275U (zh) 多股流异径管绕管式换热器
RU2378594C1 (ru) Теплообменник
US4413394A (en) Method of constructing a tube bundle
RU2153643C1 (ru) Блок опорных перегородок для труб кожухотрубного теплообменника
US20150083382A1 (en) Heat exchanger
EP3781887B1 (fr) Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur
CN118293717A (zh) 一种k形折流板换热器及其工作方法
RU2815748C1 (ru) Теплообменник с пространственно-спиральными змеевиками
RU2391613C1 (ru) Кожухотрубный теплообменник

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ PH PL PT RO RU SD SE SG SI SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP