WO1987002763A1 - Echangeur a faisceaux - Google Patents

Echangeur a faisceaux Download PDF

Info

Publication number
WO1987002763A1
WO1987002763A1 PCT/US1986/002408 US8602408W WO8702763A1 WO 1987002763 A1 WO1987002763 A1 WO 1987002763A1 US 8602408 W US8602408 W US 8602408W WO 8702763 A1 WO8702763 A1 WO 8702763A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
fluid
shell
heat exchanger
chamber
Prior art date
Application number
PCT/US1986/002408
Other languages
English (en)
Inventor
Kevin John Sulzberger
Original Assignee
Tui Industries
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 Tui Industries filed Critical Tui Industries
Publication of WO1987002763A1 publication Critical patent/WO1987002763A1/fr

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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • 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
    • F28F9/0229—Double end plates; Single end plates with hollow spaces
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/20—Fastening; Joining with threaded elements

Definitions

  • the tube temperature increases and the multi-wall tubes expand individually.
  • expansion means are needed for each individual tube. Tn addition, the design of the tube expansion means should be able to accommodate a leakage detection system.
  • U. S. Patent No. 1,683,236 to Braun discloses an integral shell and tube heat exchanger with multi-pass tube flow but only double pass shell flow directed by a single central divider. This design decreases the heat transfer efficiency because; it can not achieve complete counterflow on each pass of:shell fluid in relation to tube fluid.
  • the use of single wall tubes secured in fixed tube plates prevents efficient leak detection between the transfer fluids and does not allow for tube expansion.
  • the integral shell provides no means to reduce the thermally induced stress that causes mechanical distortion in high temperature multi-pass shell and tube heat exchangers.
  • U. S. Patent No. 1,790,828 to McKnight discloses a four-pass shell and tube heat exchanger with contraflow on each pass of the shell fluid in relation to each pass of the tube fluid.
  • This four pass contraflow is achieved through a longitudinal, vertical and horizontal baffle that extended through the shell, dividing the shell into a plurality of water tight chambers.
  • This design is satisfactory for pre-heaters where temperatures are low but not for applications requiring higher temperature refrigerants.
  • This design fails to provide for tube expansion that occurs at higher temperatures and does not take into account thermally induced mechanical distortion that occurs in high temperature shell and tube heat exchangers of the multi-pass type.
  • U. S. Patent No. 1,672,650 to Lonsdale discloses a shell and tube heat exchanger with a floating head and multiple baffles welded to an inner central tube. The ends of the baffles are fitted into resiliently packed slotted tubes which are in turn welded to the shell. Although this design achieves multi-pass shell flow, it only allows for double-pass tube flow which results in inefficient heat transfer since complete counterflow is not obtainable. The baffle and tubes can be taken out of the shell for repair and replacement, but substantial effort is required to maintain the leak-proof joint in the slotted tube which is sealed with packing.
  • GermanPatent 2,111,387 discloses a horizontal shell and tube heat exchanger.
  • Single wall tubes are used with neither leak detection nor expansion means.
  • the tubes are fixedly attached at each axial tube end to a tube plate in each end. cover.
  • a liquid or gaseous medium could be used as a shell, fzluid and radial and longitudinal baffles extend the entire length of the shell to provide for a multi-pass shell flow.
  • Radially extending partitions in the deflecting end covers provides a multi-pass flow through the tubes.
  • the longitudinal baffles are attached to a central tube which extends from one tube end plate to the other. This connecting tube increases the stability of the baffles.
  • U. S. Patent 1,738,455 to Smith discloses a steam condenser that utilizes a double walled tube.
  • a high pressure fluid flows within an outer tube wall which surrounds an inner tube wall containing a lower pressure contaminating fluid. If the inner tube leaks, the difference in pressure between the two fluids prevents fluid in the inner tube from leaking out and instead forces the higher pressure fluid to leak into the inner tube.
  • This double wall system effectively isolates the contaminating fluid when the inner tube leaks but does not provide a leakage detection system for a heat exchanger.
  • each tube end of the double wall tube configuration terminates in a separate tube plate sealed by packing.
  • the tube plates are provided with openings that are sufficiently large for the outer tubes to pass through them.
  • a disadvantage of this system is that the tube ends terminating inside each tube plate must be excessively packed to prevent leakage and the inner tube must have its tube end expanded to compensate for the tube plate modification for the outer tube.
  • British Patent 273,605 to Thornycroft discloses a steam condenser wherein the steam is condensed by a passage of coolingwater through single wall tubes that extends between two tube plates in each end of the condenser.
  • the tube ends are not fixedly attached to the tube plates and are free to longitudinally expand.
  • Each tube end is packed with packing rings which are compressed in place by ferrules.
  • the ferrules screw into each tube plate to form a watertight joint.
  • Surrounding the tube ends between the two tube plates is a fresh water chamber.
  • Smith's patent 1,738,455 if the tube end leaks, seawater inside the tubes, being at a lower pressure than the fresh water outside the tubes, cannot leak out and contaminate the fresh water.
  • TJ. S. Patent 730,284 to Pepper discloses a double wall system for a shell and tube heat exchanger that utilizes a vent chamber and bonded tubes.
  • the tube ends are fixedly attached to two tube plates at each end of the shell with a space therebetween.
  • the outside surface of the inner tube wall has helical channels or grooves cut into it so that leaking fluid can flow along the tube length to a vent chamber for detection.
  • the disadvantage of bonding is that it prevents any longitudinal expansion of the tubes and the tube ends must be fixedly attached to the tube plates to seal the vent chamber for efficient leak detection. Bonding also increases tube cost and fixedly attached tube ends prevent use of accessible and replaceable tubes.
  • U. S. Patent 2,658,728 to Evans discloses a method for longitudinal expansion of double wall tubes by having expansion joints on the shell. Evans uses two bellows type expansion * , jpints. A first joint compensates for expansion of the; oxLterr tube and a second joint compensates for the expansion. ⁇ £i the inner tube. These expansion joints increase the cost- of: shell construction and require both tube ends to be welded in respective tube plates. This construction eliminates efficient accessibility and replaceability of double wall tubes. Nor does this arrangement accommodate differential expansion of different chambers within the heat exchangers. ⁇ . S. Patent 619,585 to Newling discloses a vertical shell and tube heat exchanger with a lining between the shell and tube bundle to reduce the amount of transfer fluid that flows through the tube area.
  • the shell must be constructed with a large bore that enables the tube bundle and the floating head to be removed as a single unit in the event of repair or replacement.
  • the shell fluid inlet and outlet ports are not sealed between the shell and the lining so that a thick axially extending space contains a thick layer of stagnant shell fluid.
  • this thick layer of stagnant fluid acts as a thermal insulator it does not reduce the thermally induced stress that causes mechanical distortion in high temperature multi-pass shell and tube heat exchangers.
  • Patent 3,768,554 to Stahl discloses a vertical liquid-metal vapor generator with a wrapper sheet separating a tube bundle from the generator's shell. An annular space between the wrapper sheet and the shell shields the shell from rapid temperature transients.
  • U. S. Patent 4,114,598 to Van Leeuwen discloses a solar heater with two sided extrusions interlocked in a tongue and groove fashion. This method of interlocking is practical for solar heater elements lying in a horizontal plane but would be of no use in forming the circumferential shell of a heat exchanger. A circumferential pressure vessel shell needs three line locks to sealingly interlock the shell and a radial and circumferential segment on the extrusion to form the shell and its inner, chambers.
  • Patent 825,905 to Hellyer discloses a drying machinewhere a series of triangle cells mounted and interposed between the walls of a jacket surround a cylindrical main body portion. Although the cells are removable and form a symmetric outer shell, they have no interlocking elements or radial and circumferential segments that form a segmented and baffled self sealing shell for use in a heat exchanger of the shell and tube type.
  • a shell and tube type heat exchanger presents a relatively simple design, there are a number of problems that have reduced its overall efficiency in its present state.
  • a high quality, multi-pass heat exchanger should provide an efficient leak detection system that allows for individual longitudinal expansion of multi-walled tubes and a means to substantially reduce thermally induced stress that causes mechanical distortion while keeping the cost low.
  • a high efficiency multiple wall tube and shell heat exchanger for high pressure, high temperature fluids includes an outer pressure shell, a modular inner shell, and expansion and stress compensation to prevent mechanical distortion.
  • the modular inner shell is made out of heat conductive extrusions. Each extrusion has an integral circumferential segment and a radial baffle segment and sealingly interlocks with adjacent segments at the radially inner and outer edges to form a watertight segmented inner shell.
  • the baffle segments form internal integral axially extending baffles which are configured to provide five pass flow for shell fluid.
  • a sealed inlet and an unsealed outlet provide fluid passages for shell fluid from the interior of the inner shell to the exterior of the outer shell.
  • the outlet provides communication of shell fluid to a gap which exists between the modular inner shell and the outer pressure shell.
  • a pair of opposed end assemblies each include radial flow dividers. The end assemblies are coupled at opposed axial ends of the shell to pass a tube fluid through the tubes in five pass counterflow flow relation to the shell fluid. The end assemblies receive and seal the ends of the tubes in a stress relieving relationship.
  • the baffle segments form a plurality of chambers in the modular inner shell.
  • Each chamber receives a plurality of multi-walled helically grooved heat conductive tubes forming tube sets or tube members which extend throughout the length of the shell and into the opposed end assemblies.
  • the end assemblies are coupled at the axial ends of the shell by bolts and nuts.
  • Each multi-walled helical tube set has a thin space between the inner tube wall and the outer tube wall which channels any leaking fluid from either tube to a vent chamber in the floating end assembly which goes to the atmosphere for leakage detection.
  • the multi-walled tube sets are formed in a helical groovedesignwith precise groove dimensions to achievemaximum heat exchange efficiency between the shell fluid and tube fluid.
  • the grooves produce a turbulent flow inside the multi-walled tube which increases heat transfer efficiency by causing all portions of fluid the tube flow stream to come in contact with the wall of the inner tube.
  • the width of the groove metal to metal contact area is limited by a need for a minimum percentage of venting area within the tube, whereas the depth of the groove is such that the amount of energy needed to pump the fluid through the tube is minimal.
  • the walls of the individual tubes remain of uniform thickness to pressure optimum strength throughout the lengths of the tubes.
  • a hollow bushing is positioned around each multi-wall tube transition in each end assembly where the outer tubes; separated fxom the inner tubes.
  • the hollow bushing has two different inner diameters that correspond to the respective larger and smaller tube diameters of the multi-walled tube set.
  • Bushings in the floating end have a central radial aperture and tapered seals that sealingly fit inside the bushing at each axial end. This seal is maintained by the compression forces exerted by the tie rods and nuts which couple the end assembly to the shell.
  • Each of the two opposed end assemblies consists of a number of internal elements that are assembled in laminated fashion and secured by bolts and nuts so that access to the interchangeable elements within the shell requires minimal time and effort.
  • One of the end assemblies is called the floating end and contains a vent chamber defined between an inner tube sheet and an outer tube plate or alternatively between a tube plate and a center plate.
  • the vent chamber is positioned at a transition in the slidably coupled multi-walled tubes.
  • the floating end assembly allows each multi-walled slidably coupled tube to longitudinally expand and contract individually and apart from any other multi-wall tube.
  • a tapered seal or a bushing in the floating end couples leakage fluid to the vent chamber.
  • the other end assembly is fixed and receives the fixed ends of the multi-walled tubes in a non sliding manner.
  • the fixed end assembly also differs from the floating end assembly in that there are no tapered seals for sealing purposes but has a vent chamber for leakage detection in case of gasket failure.
  • the hollow bushing has no central radial aperture in it. Instead, a gasket is placed on each side of the bushing adjacent to the tube sheet and tube plate to form a seal. If a leak in the gasket occurs the leaking fluid will leak into the atmospheric vent chamber located at the floating end, thus preventing any possibility of contamination between the shell fluid and tube fluid.
  • the mechanical distortion that is induced by temperature differentials common in high temperature, high pressure;fluids in multi-pass shell and tube heat exchangers is m'Lnimi.z'ed by an inner shell and outer shell construction in which a thin layer of exiting shell fluid from the unsealed outlet slowly circulates in a space between the inner and outer shells.
  • This circulation reduces any temperature differential between the inner and outer shells to prevent beaming or bending of the heat exchanger.
  • This circulation also keeps any difference in temperature between the outer pressure shell and inner shell for any given segment within temperature differentials allowable to meet pressure vessel regulations.
  • the overall construction and geometry of the multi-wall, multi-pass, high temperature, high pressure heat exchanger assures high thermal efficiency with relatively low production and assembly costs while facilitating convenient replacement of component parts.
  • the exchanger is particularly suitable for applications where leakage is intolerable, such as potable water systems in which thermal energy is to be interchanged with a superheated refrigerant.
  • Figure 1 is a side elevation view, partially broken away of a heat exchanger in accordance with the invention
  • Figure 2 is an exploded perspective view of the tube fluid inlet end assembly, the opposed or outlet end assembly being substantially the same;
  • Figure 2B is a fragmentary view in perspective of the shell fluid flow within the heat exchanger with the end assembly and fluid-conducting tubes omitted;
  • Figure 3 is a cross-section of the heat exchanger taken at 3-3 of Figure 1;
  • Figure 4 is an enlarged longitudinal cross section of the fluid #1 inlet end assembly illustrating in part the heat exchange tube sealing and venting mechanisms;
  • Figure 5 is an enlarged cross sectional view of a portion of enhanced surface tubing taken about the indicated section line 5 of Figure 4;
  • Figure 6 is a cross sectional view of the fluid #1 inlet end assembly of the invention taken at 6-6 of Figure 1;
  • Figure 7 is a cross sectional view of the fluid #1 outlet end assembly of the invention taken at 7-7 of Figure 1;
  • Figure 8 is partial longitudinal cross section of the fluid #1 outlet end assembly, illustrating in part the heat exchanger tube expander bush and means of venting in case of gasket failure;
  • Figure 9 is a sectional elevation view of an alternative embodiment of a shell and tube type heat exchange in accordance with the invention.
  • Figure 10 is an enlarged fragmentary sectional view illustrating a coupling of a multi-walled tube set into opposite end assemblies.
  • Figure 11 is an exploded view of the floating end assembly of a heat exchanger in accordance with the invention;
  • Figure 12 is an enlarged cross sectional view of a portion of a triple wall tube set;
  • Figure 13 is an enlarged fragmentary sectional view illustrating a coupling of a triple wall tube set into opposite end assemblies
  • Figure 14 is a cross sectional illustration of a seal used in the floating end assembly.
  • FIG. 1 is a side elevation view of a heat exchanger 10 in accordance with the invention.
  • the heat exchanger 10 generally comprises an elongated cylindrical pressure vessel outer shell 12 that terminates in a floating end assembly 14 and a fixed end assembly 16 the floating end assembly 14 an inlet port 54 for first heat exchange fluid and the fixed end assembly 16 has outlet port 62 for the first heat exchange fluid.
  • a first thermal exchange fluid such as relatively cold potable water, is to enter the heat exchanger 10 through the inlet port 54 make a multipass flow through shell 12 and exit through the outlet port 62.
  • a second thermal exchange fluid such as a superheated refrigerant (i.e., ammonia or halocarbon) is applied through an inlet port 18 providing an aperture through a neck flange 46 which forms an end portion of shell 12 at a fixed end thereof adjacent fixed end assembly 16.
  • the second fluid makes a multi-pass flow through shell 12 contra to the first fluid and then exits the heat exchanger shell 12 through an outlet port 20 in a neck flange 44.
  • the neck flange 44 forms a portion of shell 12 at a floating end thereof adjacent the floating end assembly 14.
  • Theouter pressure vessel shell 12 is shown partially broken in Figure 1, exposing a substantially cylindrical inner modular shell 22 having baffled chambers which may also be referred to as subchambers.
  • T e floating end assembly 14 is illustrated in greater detail in Figures 2A and 2B, to which reference is now made.
  • a plurality of multi-walled heat exchange tube sets or members 75 are positioned within the modular shell 22 which is partitioned by a longitudinally extending baffle assembly 74 the baffle assembly 74 operates to effect a multi-pass, counterflow flow path for the second heat exchange fluid.
  • the counter flow flow path optimizes a thermal exchange, between the first fluid within the multi-walled tubes 75 and second fluid within the modular shell 22.
  • the assemblies for such purpose are illustrated in greater detail in subsequent drawing figures.
  • neck flanges 44 and 46 are affixed to axially opposed ends of the pressure vessel shell 12 by welding or an equivalent process.
  • the neck flanges 44, 46 are conveniently identical in structure, but are rotatably offset 72° from each other prior to affixation to the shell.
  • the end assemblies 14, 16 respectively comprise a laminated arrangement of elements joined to neck flanges 44 and 46 respectively by a plurality of bolts 48 peripherally arranged about the end assemblies 14 and 16 and threadedly engaged to center pressure flange 32 and 34 then engaged to nuts 50.
  • the floating end assembly 14 includes an end cap 24, a center pressure flange or center plate 32, an inner tube sheet or plate 40 and a flange gasket 69 which seals end assembly 14 to the shell 10.
  • a tube plate gasket 67 & 68 seal the center plate 32 to the tube plate 40 and a cap gasket 29 seals cap 24 to the center plate 32.
  • the fixed end assembly 16 similarly includes an end cap 26, a center pressure flange or center plate 34, and an inner tube sheet or tube plate 42. Fixed end assembly 16 is sealed by a set of gaskets which correspond to those described for the floating end assembly 14 and are therefor not described in detail.
  • the neck flange 44 conveniently includes exit port 20, through which the second heat transfer fluid exits, as well as a port 85 for a pressure relief valve 86. Both ports
  • HEET communicatewith themodular shell 22 as subsequently described in greater detail.
  • the ports may be formed as part of a casting process by which the flange is conveniently made this provides a less expensive alternative to drilling apertures in the-shell 12 and welding to the shell 12 internally threaded fittings.
  • the axially extending, chamber partitioning baffle assembly . T4* which also forms the circumferial wall of the modular * shell 22, partitions the modular shell into five fluidtight axially extending chambers.
  • Each of the five chambers encloses a defined group or nest of multi-walled heat exchange tube sets 75.
  • FIG 3 is a cross-section of the heat exchanger 10 taken along line 3-3 in Figure 1.
  • the baffle assembly 74 is seen to be formed from five slidably but sealingly double interlocking baffle member extrusions 76, 78, 80, 82 and 84 which may be simply and economically formed from, for example, aluminum via an extrusion process.
  • extrusion 76 is seen to comprise an integral radially extending arm 134 and a circumferentially extending arm 132 that forms a segment of inner shell 22 and conforms generally to the inner circumference of the pressure vessel shell 12.
  • Each integral circumferential arm 132 and radial arm 134 of each extrusion extends axially through the pressure vessel shell 12.
  • the five circumferential arms form the outer periphery of the modular shell and the five radial arms form the inner fluidtight baffled chambers.
  • the circumferential arm 132 of extrusion 76 extends generally circumferentially away from the radial arm 134 and sealingly joins the radially extending arm of adjacent extrusion 78 at a radially outer edge 140.
  • the radial arm 134 of extrusion 76 sealingly joins the circumferentially extending arm of adjacent extrusion 84 at a radially outer edge 138.
  • each extrusion 76, 78, 80, 82 and 84 engages an extreme edge of a cantileveled circumferentially extending arm of an adjacent extrusion to form the inner shell 22.
  • a generally circular axially extending head engages a generally circular, axially extending aperture to provide an axially slidable seal between the two mating members.
  • extrusion 76 lies interjacent extrusions 84 and 78, with extrusion 84 being adjacent in a clockwise direction and extrusion 78 being adjacent counter clockwise.
  • the radially inner portion of the radial arm 134 terminates in a hook shape adapted to interlock with a mating recepticle appendage of the radial arm of the counter-clockwise adjacent extrusion 78.
  • a recepticle appendage 137 is adapted to sealingly, but slidably interlock with the terminus of the clockwise adjacent radial arm of the extrusion 84. As shown in Figure 3, each radial arm butts against its adjacent neighbors and sealingly interlocks at both radially inward and radially outward edges thereof.
  • baffle assembly 74 Construction of the baffle assembly 74 is particularly inexpensive.
  • a first extrusion 84 is placed inside the shell 12.
  • the distal end of a second extrusion such as extrusion 76 is matingly aligned with the proximal end of the first extrusion and axially slid into mating engagement with the first extrusion 84.
  • the shape of the interlocking beads and apertures precludes separation except by relative sliding of adjacent extrusions in the axial direction.
  • Each of the third through fifth members is thereafter slid axially into place to complete the baffle assembly 74.
  • the radially extending arms of the baffle members are slightly oversized to provide a radially directed compression of the assembly, effecting a seal where the radial arms abutt.
  • T e circumferential arms of the extrusions include radially outward extending legs 76a, 78a, 80a, 82a and 84a
  • FIG. 3 additionally illustrates a cross-section of the inlet 18 for the second heat exchange fluid and multi-walled tube sets 75 for conducting the first heat exchange fluid.
  • the second heat exchange fluid enters the baffle chamber * designated Sector I defined by extrusion 84 and radial arm 134, and flows axially out of the drawing.
  • the inlet 18 includes an aluminum sleeve 71 which is sealingly passed through the aperture in the pressure vessel shell 12 into inlet 18 and expanded into position.
  • the inlet 54 for the first heat exchange fluid is oriented to couple incoming fluid into a nest or group of tube sets 75 occupying the chamber designated Sector v defined by the baffle assembly.
  • the baffle assembly 74 directs the second fluid sequentially in alternate axial directions through the chambers designated I, II, III, IV and V.
  • the tube sets 75 and associated manifolding chambers formed by the end assemblies 14, 16 direct the first fluid in sequential and alternating counter flow axial directions through the chambers designated Sector V, IV, III, II and I.
  • each multi-walled tube set 75 generally comprises at least an outer tube or wall
  • this invention provides a particular configuration wherein the controlling parameters are optimized.
  • a groove width 122 of approximately 1/8 inch and depth of approximately 3/32 inch assures good turbulation of the fluids on both sides of the tube set 75 while maximizing heat transfer without collapsing the tube set 75 during manufacture.
  • the pitch 124 of the optimal tube is found to be 9/16 inch.
  • a gap 110 of .003 inches was employed to meet venting regulations but should be kept at a minimum to ensure maximum heat transfer.
  • each tube set 75 could include three
  • SUBSTITUT or more tubes for added safety, or protection from fluids hostile to the tube material.
  • the inner tube plate 40 is first mounted onto the neck flange 44 by means of positioning dowels 70 protruding from the neck flange 44.
  • the dowels 70 receive the neck flange gasket 69 and tube plate 40.
  • the dowels and dowel-receiving holes are similar to dowel 70 and holes 56 associated with tube plate 40 of the inlet assembly 14 and illustrated in Figure 2A.
  • the tube plate 42 which is similar to plate 40 (Fig. 2A) includes a pattern of holes sized to accommodate the outer tubes 96 of the tube sets 75.
  • the hole pattern corresponds to the pattern of the multi-walled tube sets 75 shown in figure 3.
  • FIG 8 a fragmentary sectional view of the fixed end of the heat exchanger 10.
  • the bushing 104 includes a through-hole having a stepped wall 104a such that the larger internal diameter portion of the bushing engages the outer tube 96 of the multi-walled tube set 75, while the smaller diameter portion of the bushing engages the inner tube 57 of multi-walled tube set 75.
  • a general swedging tool may then be inserted into the tube, as is known in the art, to expand the tubes within the bushing and thereby effect respective seals between the bushing and the inner and the outer tubes, with the gap 110 between the inner and outer tubes being sealed against the step 104a of the internal bushing wall.
  • the neck flange 44 is shown to include a number of peripheral apertures 33 and an axially or longitudinally extending, peripheral dowel 70.
  • the dowel 70 is adapted to pass through positioning holes respectively formed in the components of end assembly 14 when the components are mounted onto the flange 44.
  • an assembly comprising a gasket 69, a tube plate 40 interjacent two gaskets 68, 67 is mounted onto the neck flange 44.
  • the tube plate 40 and gasket 68 include aligned hole patterns corresponding to the layout of tube holes 95 so that the tube sets 75 extend outward therethrough.
  • the gasket assembly and the corresponding gasket assembly of outlet assembly 16 define the ends of the flow path for the second heat transfer fluid.
  • each bushing 41 includes a pair of spaced apart O-rings 102, 103 for forming a tube expansion region 43 communicating with gap 110 in multi-walled tube 75.
  • a radial hole 111 through bushing 41 which connects to gap 110 to a vent 45 chamber formed between tube plate 40 and center plate 32 to allow the tube to vent to atmosphere.
  • gasket 67 is fitted over the protruding inner tubes 57 of tube sets 75.
  • a center plate 32 is then correctly oriented via dowel 70 and assembled onto the neck flange 44.
  • the axially inner face of center plate 32 butts against the gasket 67 which is against the outer face of the bushings 41, resulting in an outer annular portion 32a which circumvents
  • bushing 41 includes a through-hole 111 through which any fluid in gap 110 will escape.
  • the escaping fluid falls downward through chamber 45 and out of the end assembly via through-hole 47 in the bottom periphery of the pressure flange 32 and is detected by means hereinafter set forth so that the multi-walled tube 75 can be replaced before a subsequent fracture in inner tube 57 or other event permits a mixing of the first and second fluids.
  • a fracture of the inner tube 57 results in first fluid being restricted to region 43 and escaping via hole 111 and 47.
  • the center plate 32 additionally comprises a central portion 32b relatively recessed from the gasket-contacting surface of the annular portion 32a.
  • the recessed portion contains a pattern of through-passages 95 located in alignment with the ends axially extending inner tubes 57 that protrude from bushings 41.
  • the axially inward face of the recessed portion 32b surrounds each passage 95 thereby sealingly contacts the axially outward face of the respective bushing against gasicet 67.
  • the ends inner tubes 57 extend into, but do not protrude from the axially outward side of, passages 95.
  • the axially outer face of the center plate 32 includes an end baffle arrangement 28 comprising an annular portion 28a circumscribing the through-holes 95 together with a generally Y-shaped portion comprising generally radially extending bars 52a, b, and c.
  • the bars 52a, b, and c, and annular portion 28a are adapted to sealingly contact the interior face of end cap 24 via a gasket 29 and to thereby form a * series of pressure chambers, as better explained by reference to Figures 6 and 7.
  • Figures 6 and 7 are cross-sectional views of portions of the inlet and outlet end assemblies taken along the lines 6-6 and 7-7, respectively, of Figure 1. As can be seen, the end assemblies are substantially similar.
  • the plurality of bolt receiving holes 149 is provided about the outer periphery of pressure flange 32, 34.
  • End baffle 28, 30 illustrated in Figures 6 & 7 as comprising an annular steel portion 28a, 30a, with radial vane arrangements 52a, b, c, and 59a, b, c.
  • the relative orientations of the vanes 28, 30 by a 72° rotational offset.
  • Apertures 56, 38 in the annular portion of the baffles are provided for insertion about positioning dowels 70, 70' to provide the correct relative orientations of the vane arrangements within the end assemblies 14 and 16. Accordingly, the welding of neck flange 46 onto shell 12 at a rotational offset of 72° from the orientation of neck flange 44 permits identical components to be used in end assemblies 14, 16 except for bushings 41, 104.
  • the end baffles 28, 30 vanes define pressure chambers in the end assemblies 14, 16 that provide a fluid flow continuum or manifold for reversing the direction of the first heat exchange fluid within the thermal exchange tubes.
  • the dashed circles 54 and 62 indicate the locations of the inlet port 54 and the outlet port 62 with respect to the vane arrangements 28 and 30 respectively.
  • the radial fins of each arrangement subtend two obtuse and acute angle. In an actual reduction to practice of the invention, an acute angle of 72° and obtuse angles of 144° were employed.
  • the through passages 95 which the ends of the inner tube 57 engage into are shown in Figures 6 and 7.
  • the axially outer faces 28a, 30a are illustratively divided into in 72° segments denoted "A" through “E” and “A 1 " through “E' ⁇ , respectively.
  • the three radial vanes of each end baffle cooperate with the interior of the respective end cap 24, 26 to define 3 end chambers at each end of the heat exchanger.
  • the flow of the first heat exchange fluid through the heat exchanger occurs in the following sequence: the fluid enters the heat exchanger 10 under pressure at inlet port 54 ( Figure 6), distributing itself over the 72° section A to thereby enter inner tube 57 group of heat transfer multi-walled tubes 75 that are telescopically engaged within the passages 95 of the pressure plate 32.
  • the fluid then travels in the tubes through the heat conductive modular shell 22 to the 144° section of the pressure chamber in the outlet end assembly 16 comprising the A* and E' segments (Fig. 7).
  • the fluid emerges from the tubes in section A 1 under pressure, its only outlet from this section of the end chamber is the path commencing with the set of channels of section E' , through which it enters inner tubes 57 that transport the fluid back through the modular shell 22 to the inlet end 14 section.
  • Emerging from the pipes of segment B (Fig. 6) the fluid can only enter the channels within segment C for transmission once again through the heat exchange chamber 22, and so forth.
  • the radial armof extrusion 78 terminates short of tube sheet 42, permitting the second fluid to pass into section III and flow towards the inlet end 14 ( Figure 1). From section III, the second fluid similarly flows through section IV and V egressing from the modular shell 22 via outlet 20 at the completion of its pass through section V.
  • Figure 3 displays a "dot” and "cross” symbol in a representative multi-walled tube 75 of each nest group to indicate the flow direction of first fluid in the respective segment.
  • a “dot” indicates flow out of the plane of the page, while a “cross” indicates a flow into the plane.
  • the flow direction of the second fluid is shown by a like symbol in each segment exterior to the tube set 75 therein.
  • the first and second fluids flow in opposite directions in each of the sections i-v.
  • the first fluid will be at one temperature extreme (e.g., coldest) in section V, and progressively hotter (to follow the example) in each successive section IV-I as it flows through successive segments in a clockwise direction.
  • the second fluid is at its temperature extreme (e.g., hottest) in section I, wherein the first fluid is hottest flows through successive segments in a counter-clockwise direction, and exits from section-V, at its coldest, where the first liquid is also at its * coldest.
  • the two fluids continue to exchange heat unidirectionally throughout their counterflow in the heat exchanger.
  • a thin circulating layer of second fluid is provided in the annular, axially extending space 145 between the circumferential arms of the baffle assembly and the inner circumferential wall of modular shell 22.
  • legs 76a, 78a are, as previously mentioned, provided by legs 76a, 78a,
  • the outlet 20 for the second fluid does not include a sleeve such as sleeve 71 of inlet 18, thereby permitting egressing second fluid to "leak" into, and fill, the space. Accordingly, the temperature of the shell is maintained generally uniform about its circumference.
  • the second fluid (assumed to be refrigerant for illustrative purposes) in segment I is warmest, is successively colder in segments II-V. Accordingly, the second fluid in space 145 radially adjacent to section I will be warmer, and less dense, than the second fluid in space 145 radially adjacent to section V.
  • the second fluid in space 145 will tend to rise counter-clockwise in Figure 3. Once the second fluid reaches the 12 o'clock position, gravity causes it to flow downward, completing the loop. Once the space is filled, no additional fluid enters the space, and fluid in the space will slowly circulate counter-clockwise to minimize temperature-induced stresses in the shell.
  • the end assemblies of the heat exchanger 10 are completed by positioning the end caps 24, 26 onto the neck flange 44, 46 respectively.
  • Bolts 48 are inserted through the apertures 33 in both neck flanges with their heads pointed opposite the heat exchanger. Nuts 50 are then tightened onto the bolts to secure the end assemblies 14, 16.
  • the holes 149 in the pressure flanges 32, 34 are threaded to engage the bolts 48. Accordingly, the removal of nuts 50 permits disassembly of the end caps 24, 26 for visual inspection of the end baffles without breaking the seal between the (pressure) ) flanges 32, 34 and respective neck flanges 44, 46.
  • the tubes 75 may accordingly be inspected through apertures 95 without the voiding of the second fluid in the modular shell 22. This is particularly advantageous when the second fluid is a refrigerant.
  • end assemblies can be easily disassembled.
  • the expanded tube/bushing combination requiring replacement can simply be axially slid out of the heat exchanger with the seals of the bushing 41 permitting the axial sliding movement.
  • a replacement bushing/expanded tube combination can then be axially slid through the inner tube sheet 42, modular shell 22, inner tube sheet 40 and the bushing 41 with seals refitted to the replaced tube combination.
  • end assembly 16 Figure 8
  • Another feature of ' the described embodiment is directed to the temperature-induced dimensional changes in the tube sets 75.
  • higher outlet temperatures of the first fluid have been provided using a five segment modular shell with successive counterflowing first and second fluids to increase surface contact time.
  • the tube sets 75 of each segment will expand to a greater or lesser degree than the tubes of the remaining segments. Accordingly, the aforedescribed configuration permits each tube set 75 to freely expand to the extent required, thereby meeting design codes governing such heat exchangers.
  • the tube ends in end assembly 16 are relatively fixed owning to the securing of bushings 104 into which the tubes have been expanded.
  • the other end of the tube set 75 are permitted to "float" axially so that temperature-induced changes in standardized tube length may be accommodated during operation of the heat exchanger.
  • outer tube 96 of multi-walled tube 75 may slide axially within the O-ring or tappered seal without loss of sealing contact therebetween.
  • inner tube 57 may slide axially within the O-ring or tapered seal without loss of sealing contact between the two. Because tube 57 and tube 96 are joined together by metal contact area 122, multi-walled set tube 75 is one tube of a tube within a tube design and tubes 57 and 96 move simultaneously.
  • the heat exchanger thereby herein meets all known potable water codes or regulations as well as the design specification of the ASME pressure vessel codes in the United States, and corresponding foreign codes.
  • Tube plates 240, 242 are generally cylindrical flat plates with enlarged diameters enabling them to receive locating pins 270 and bolts 248.
  • Annular flange gaskets 269A, 269B seal the periphery of tube plates 240, 242 against the neck flanges 44, 46.
  • Center plates 232, 234 have a central disk shaped region with an annular flange 232A, 234A extending axially inward to engage the axially outward side of tube plates 240, 242..and form chambers 280, 282 in the interior thereof.
  • the transitioning ends of the tube sets 75 are sealed within the chambers 280,.2.82 and form a vent chamber for leakage fluid through vent holes 247.
  • center plates 232, 234 have axially annular flanges 284, 286 extending axially outward to be sealed against end plates 224, 226 by cap gaskets 229A, 229B respectively. Ridges or vanes 52A are formed within the annuli 284, 286 to define manifolding chambers for directing the first heat exchange fluid from one group of tube sets 75 to a next sequention group of tube sets 75.
  • a bushing 241 has a small tapered or champered axial bore at the axiallyoutward end for receiving a seal 241B which sealingly, but slidably engages the inner tubes 57.
  • a larger, axially extending bore extends partway through bushing 241 from the axially inward end to slidingly receive sea; 241A which seals the outer tube 96.
  • bushings 204 fixedly seal the tube sets 75 to tube plate 242 and center plate 234 in a manner substantially identical to the sealing provided by bushings 104.
  • Figs. 12 and 13 the spiraling and sealing of a triple wall tube set are shown as including a triple wall tube set 375 having a stainless steel inner tube 300, a copper center tube 302, and a stainless steel outer tube 304.
  • the spiral groove deformation 306 is swaged into the set after the three tubes of a set are concentrically assembled and has a width of 0.165 inch as indicated at central region 308, a pitch 310 of 9/16 inch and a depth of 3/16 inch.
  • the deformation leaves spiraling air gap channels 312, 314 having a width of approximately 0.375 inch.
  • the outer tube 304 has a nominal outside diameter of 3/4 inch and a wall thickness of 0.020 inch. After swaging of the groove 306 outer tube 304 is centerless ground to an actual diameter of 0.749 inch to assure circular ends that will properly seal.
  • the centerless grinding typically reduces wall thickness by approximately 0.001 inch and slightly improves the heat transfer characteristics of the relatively poor heat conducting 321 type stainless steel outer tube 304 by reducing its thickness.
  • the center tube 302 is made from 98% pure copper and is ground from 0.716 inch to an outside diameter of 0.710 inch prior to assembly into outer tube 304. Center tube 302 has an inside diameter of approximately 0.628 inch. The air channel between outer tube 304 and center tube 302 is thus approximately 0.002 inch thick.
  • the copper center tube 302 primarily serves as a thermally conducting filler between the standard sizedouter tube304 and standard sized inner tube 300.
  • Inner tube 300 is made of type 316 passivated stainless steel with a nominal outside diameter of 5/8 inch and is centerless ground to an outside diameter of 0.624 inch with a wall thickness of approximately 0.021 inch. This allows the leakage channel 314 to have a thickness of approximately 0.002 inch.
  • the triple wall tube set 375 thus has a nearly optimum turbulance inducing roughness in the inside of inner tube 300. While the roughness increases frictional pressure loss, it increases heat transfer efficiency.
  • a particularly large heat transfer enhancement can be obtained from a rounded helical ridge having a ridge inside diameter to base tubes inside diameter ratio 0.907 and a pitch to inside tube diameter ratio of 0.95.
  • the swaged groove 306 provides inner tube 300 with an internal helical ridge which matches these optimum ratios.
  • outer tube 304 and inner tube 300 are made of stainless steel to provide corrosion resistance against refrigerants and water in the present example, other materials may be used in conjunction with different heat exchange fluids. For some applications, special materials such as titanium may be required to attain adequate corrosion resistance.
  • a floating end assembly 320 includes a center plate 322 and a tube plate 324 defining a vent chamber 326 between them.
  • Inner tube 300 is received by an axial bore 326 in center plate 322 and outer tube 3.04 is received by a larger axial bore 328 in tube plate 324.
  • a bushing 330 is placed on the tube set 375 end transition between the center plate 322 and tube plate 324 and has a radially extending vent bore 332 to carry any leakage fluid from the transition to the vent chamber 326.
  • Bushing 330 has a smaller diameter axial bore 336 adjacent center plate 322 which matingly receives inner tube 300 and a larger diameter axial bore 338 adjacent tube plate 324 and extending axially past bore 332 whichmatingly receives outer tube 304.
  • a radiused recessed cavity or chamfer 340 is formed at the outer end of small bore 336 which receives a seal 342 which seals the inner tube 300 to the inner surface of center plate 322.
  • the large bore 338 has a radiused recessed cavity or chamfer 350 which receives a seal 352 which seals outer tube 304 against the outer surface of tube plate 324.
  • This floating end sealing arrangement eliminates double O-ring seals which can be severed during assembly. It is impossible to detect this occurrance until a heat exclnanger is fully assembled and tested for leakage. When leakage occurs the leaking seal must be identified and then replaced at substantial expense.
  • FIG. 14 A cross sectional view of seal 342 prior to compression is shown in Fig. 14.
  • the seal 342 has a 90° angle 360 between a cylindrical inner diameter face 362 which matingly receives inner tube 300 and an annular or disk shaped flat surface 364 which engages center plate 322.
  • the seal 342 is preferably made of a commercially available Viton material.
  • Each of the faces 360, 362, 364, 366 have a minimum length of 0.050 inch while the thickness 365 is a minimum of 0.071 inch and the length 367 is approximately 0.212 inch.
  • a minimum width to length ratio of aproximately 0.30 and preferably of 0.33 must be maintained to prevent seal 342 from backling along faces 369 and 371 under the sealing forces.
  • the chamfer of bushing 330 has a radius 331 defining a chamber 331A which, along with a chamber 331B, provides room for thermal expansion of seal 342.
  • the inner diameter of seal 342 is 0.564 inch to require a stretch fit of cylindrical face over the 0.624 inch inner tube 300 to assure a sealing force against the periphery of tube 300.
  • the inside diameter should be stretched between 17 and 22 percent to maintain proper sealing force.
  • the compressive force of bushing 330 forces face 364 into sealing contact with center plate 322.
  • the face 364 should be compressed between 17 and 22 percent relative to an axial width 369 to maintain a proper sealing force.
  • a component of this sealing force is transmitted through seal 342 to create additional sealing force at tube sealing face 362.
  • the construction of seal 350 is similar except that the inside diameter is larger to accommodate the larger outside tube 304.
  • a fixed end assembly includes a tube plate 380 and a center plate 382 having the fixed end transition sealed therebetween by a bushing 384.
  • Bushing 384 has a small axial bore 386 which matingly receives inner tube 300 and a large axial bore 388 which matingly receives outer tube 304.
  • bushing 384 is pushed over the fixed end of a tube set 375 and then the tubes are expanded in the vicinity of the bores 386, 388 to secure a fluid tight seal. The tubes are then inserted into gasket 3,68.
  • Gasket 367 and center plate 382 are then assembled to secure a seal of outer tube 304 against the gasket 368 and outer surface of tube plate 380 and a seal of inner tube 300 against gasket 367 and center plate 382.

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

Un échangeur à faisceaux (10) permettant d'obtenir le passage multiple à contre-courant de deux fluides échangeurs de chaleur comprend une enceinte extérieure cylindrique (12), un agencement modulaire à chicanes (74) pour guider le fluide dans l'enceinte, une pluralité d'ensembles de tuyaux (75) à parois multiples et une paire d'agencements terminaux opposés (14, 16). Un agencement terminal fixe (16) reçoit de manière inamovible une extrémité des ensembles de tuyaux (75) et exerce une fonction de distribution (59a, 59b, 59c), en dirigeant l'écoulement du fluide dans les ensembles de tuyaux lors de passages multiples. Un agencement terminal opposé et flottant (14) reçoit par glissement et rend étanches les extrémités flottantes des tuyaux afin de permettre leur expansion et leur contraction induites par des changements de la température. L'agencement terminal flottant (14) exerce également une fonction de distribution (59a, 59b, 59c), en dirigeant l'écoulement du fluide dans les ensembles de tuyaux (75) lors de passages multiples. Un ensemble (375) de tuyaux à paroi triple peut être utilisé afin d'assurer une protection supplémentaire contre la contamination des fluides échangeurs de chaleur.
PCT/US1986/002408 1985-11-05 1986-11-04 Echangeur a faisceaux WO1987002763A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US79524085A 1985-11-05 1985-11-05
US795,240 1985-11-05

Publications (1)

Publication Number Publication Date
WO1987002763A1 true WO1987002763A1 (fr) 1987-05-07

Family

ID=25165084

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1986/002408 WO1987002763A1 (fr) 1985-11-05 1986-11-04 Echangeur a faisceaux

Country Status (3)

Country Link
EP (1) EP0245465A4 (fr)
JP (1) JPS63502847A (fr)
WO (1) WO1987002763A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1014026A3 (fr) * 1998-12-23 2001-08-22 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Echangeur de chaleur pour préchauffer un gaz oxydant
EP1113238A3 (fr) * 1999-12-28 2003-11-12 Nippon Shokubai Co., Ltd. Echangeur de chaleur à tubes et calandre
US8661674B1 (en) 2010-12-15 2014-03-04 Michael P. Metz Method of repairing a furnace
US10030887B2 (en) 2012-05-13 2018-07-24 Aerco International, Inc. Water heating apparatus with parallel heat exchangers
US10119724B2 (en) 2009-12-23 2018-11-06 Fueltech Sweden Ab Accumulator tank
US10704802B2 (en) 2012-05-13 2020-07-07 Aerco International, Inc. Water heating apparatus with parallel heat exchangers
CN112902734A (zh) * 2021-03-16 2021-06-04 西安交通大学 一种应用于高温高压下的矩形窄缝通道流通结构

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03122494A (ja) * 1989-10-02 1991-05-24 Tooshin Technical:Kk 原料の予熱及び冷却装置
JP4623243B2 (ja) * 1998-10-05 2011-02-02 株式会社ニコン 電磁アクチュエータ及びステージ装置
JP2013108686A (ja) * 2011-11-22 2013-06-06 Mdi Corp シェルアンドチューブ熱交換器
CN103822510B (zh) * 2014-03-07 2016-04-13 中石化上海工程有限公司 多壳程列管式换热器
SE544878C2 (en) * 2021-01-20 2022-12-20 Marinnovation Hb Tube heat exchanger

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB273605A (en) * 1926-02-12 1927-07-12 Thornycroft John I & Co Ltd Improvements in or relating to steam condensers
US1738455A (en) * 1927-12-10 1929-12-03 Gen Electric Steam condenser
US2000653A (en) * 1932-12-21 1935-05-07 Crane Packing Ltd Heat exchange apparatus
US2187555A (en) * 1936-12-01 1940-01-16 Gen Electric Surface cooler
US2658728A (en) * 1948-06-25 1953-11-10 Lummus Co Method of detecting leakage between heat transfer fluids
GB730284A (en) * 1951-11-16 1955-05-18 Foster Wheeler Ltd Improvements in and relating to heat exchangers
DE2111387A1 (de) * 1971-03-03 1972-09-07 Karl Fischer App U Rohrleitung Rohrbuendel-Waermeaustauscher
DE2442027A1 (de) * 1974-09-03 1976-03-25 Steinmueller Gmbh L & C Roehrenwaermeaustauscher
DE2742877A1 (de) * 1977-09-14 1979-03-22 Sulzer Ag Waermeuebertrager, insbesondere rekuperator fuer hochtemperaturreaktoren

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1919141U (de) * 1965-03-26 1965-07-08 Buderus Eisenwerk Boiler oder kessel.
FR1521334A (fr) * 1966-05-04 1968-04-19 Brown Fintube Co Raccord de conduites
FR1537988A (fr) * 1967-07-12 1968-08-30 Danto Rogeat & Co Perfectionnement aux échangeurs thermiques tubulaires
AU7757581A (en) * 1980-11-19 1982-05-27 United Energy Technologies Inc. Enhanced surface tubing
NZ198291A (en) * 1981-05-22 1984-10-19 Energy Resources International Fixed tube sheet exchanger with at least three contraflow shell and tube passes
EP0120497B1 (fr) * 1983-03-28 1989-07-26 Tui Industries Echangeur de chaleur à enveloppe et tubes

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB273605A (en) * 1926-02-12 1927-07-12 Thornycroft John I & Co Ltd Improvements in or relating to steam condensers
US1738455A (en) * 1927-12-10 1929-12-03 Gen Electric Steam condenser
US2000653A (en) * 1932-12-21 1935-05-07 Crane Packing Ltd Heat exchange apparatus
US2187555A (en) * 1936-12-01 1940-01-16 Gen Electric Surface cooler
US2658728A (en) * 1948-06-25 1953-11-10 Lummus Co Method of detecting leakage between heat transfer fluids
GB730284A (en) * 1951-11-16 1955-05-18 Foster Wheeler Ltd Improvements in and relating to heat exchangers
DE2111387A1 (de) * 1971-03-03 1972-09-07 Karl Fischer App U Rohrleitung Rohrbuendel-Waermeaustauscher
DE2442027A1 (de) * 1974-09-03 1976-03-25 Steinmueller Gmbh L & C Roehrenwaermeaustauscher
DE2742877A1 (de) * 1977-09-14 1979-03-22 Sulzer Ag Waermeuebertrager, insbesondere rekuperator fuer hochtemperaturreaktoren

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0245465A4 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1014026A3 (fr) * 1998-12-23 2001-08-22 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Echangeur de chaleur pour préchauffer un gaz oxydant
EP1113238A3 (fr) * 1999-12-28 2003-11-12 Nippon Shokubai Co., Ltd. Echangeur de chaleur à tubes et calandre
US10119724B2 (en) 2009-12-23 2018-11-06 Fueltech Sweden Ab Accumulator tank
US8661674B1 (en) 2010-12-15 2014-03-04 Michael P. Metz Method of repairing a furnace
US10030887B2 (en) 2012-05-13 2018-07-24 Aerco International, Inc. Water heating apparatus with parallel heat exchangers
US10704802B2 (en) 2012-05-13 2020-07-07 Aerco International, Inc. Water heating apparatus with parallel heat exchangers
CN112902734A (zh) * 2021-03-16 2021-06-04 西安交通大学 一种应用于高温高压下的矩形窄缝通道流通结构
CN112902734B (zh) * 2021-03-16 2024-05-28 西安交通大学 一种应用于高温高压下的矩形窄缝通道流通结构

Also Published As

Publication number Publication date
EP0245465A1 (fr) 1987-11-19
EP0245465A4 (fr) 1988-04-18
JPS63502847A (ja) 1988-10-20

Similar Documents

Publication Publication Date Title
US4858681A (en) Shell and tube heat exchanger
US4871014A (en) Shell and tube heat exchanger
US5323849A (en) Corrosion resistant shell and tube heat exchanger and a method of repairing the same
WO1987002763A1 (fr) Echangeur a faisceaux
WO2005001368A2 (fr) Protection anticorrosion de plaques tubulaires d'echangeur thermique
CA1264735A (fr) Echangeur thermique a tubulure sous enveloppe
US5174369A (en) Sanitary concentric tube heat exchanger
US3593782A (en) Heat exchanger
US3768550A (en) Heat exchanger
GB2041191A (en) Heat exchanger
CN210292957U (zh) 换热器密封结构及换热器
US2607567A (en) Heat exchanger
EP0113344B1 (fr) Echangeurs de chaleur et leur procede de construction
US3735810A (en) Plate heat exchanger
EP4184107A1 (fr) Echangeurs thermiques a assemblage thermoretractable
US3734176A (en) Heat exchanger assembly having a common fluid box
US11512902B2 (en) Flow baffles for shell and tube heat exchangers
WO1993003318A1 (fr) Echangeur de chaleur du type a baïonnette
US5518066A (en) Heat exchanger
EP3645953B1 (fr) Échangeur de chaleur pour conditions de service sévères
US4318441A (en) Counterflow heat exchanger
US11306972B2 (en) Shell and tube heat exchangers
CN214308336U (zh) 一种管壳式多程换热器
JPS59189290A (ja) 熱交換器
JPH0113274Y2 (fr)

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BE DE FR GB NL

WWE Wipo information: entry into national phase

Ref document number: 1986907141

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 1986907141

Country of ref document: EP

WWW Wipo information: withdrawn in national office

Ref document number: 1986907141

Country of ref document: EP