EP0259895B1 - Rohrbündelwärmetauscher - Google Patents

Rohrbündelwärmetauscher Download PDF

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Publication number
EP0259895B1
EP0259895B1 EP19870113723 EP87113723A EP0259895B1 EP 0259895 B1 EP0259895 B1 EP 0259895B1 EP 19870113723 EP19870113723 EP 19870113723 EP 87113723 A EP87113723 A EP 87113723A EP 0259895 B1 EP0259895 B1 EP 0259895B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
bushing
walled
tubes
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.)
Expired
Application number
EP19870113723
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English (en)
French (fr)
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EP0259895A1 (de
Inventor
Kevin Sulzberger
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TUI Industries Inc
Original Assignee
TUI Industries Inc
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Filing date
Publication date
Application filed by TUI Industries Inc filed Critical TUI Industries Inc
Publication of EP0259895A1 publication Critical patent/EP0259895A1/de
Application granted granted Critical
Publication of EP0259895B1 publication Critical patent/EP0259895B1/de
Expired legal-status Critical Current

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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
    • F28F9/0229—Double end plates; Single end plates with hollow spaces
    • 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
    • F28D7/16—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 being arranged in parallel spaced relation
    • F28D7/163—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 being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—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 being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • 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
    • F28F1/003—Multiple wall conduits, e.g. for leak detection
    • 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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • F28F9/22—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 present invention relates to a heat exchanger as defined in the precharacterizing portion of claim 1.
  • a heat exchanger of this kind is already known from EP-A 0 052 522. Said heat exchanger comprising
  • 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 outer shell 12 that terminates in end assemblies 14 and 16, the former assembly being denoted the inlet end assembly and the latter the outlet end assembly in recognition of the fact that the invention contemplates that a first thermal exchange fluid, such as relatively cold potable water, is to enter the heat exchanger 10 through an inlet port 54 in the end assembly 14 and exit through an outlet port 62 in the end assembly 16.
  • a first thermal exchange fluid such as relatively cold potable water
  • a second thermal exchange fluid such as a superheated refrigerant (i.e., ammonia) is applied through an inlet 18, comprising an aperture in a neck flange 46.
  • the second fluid thereafter exits the heat exchanger through an outlet 20 in the neck flange 44.
  • the outer shell 12 is shown partially broken in Fig. 1, exposing a substantially cylindrical inner chamber 22.
  • the device as shown in Fig. 1 is not a complete assembly; as will be described in greater detail, and as illustrated in Fig. 2, a plurality of heat exchange multi-walled tubes 75 and a chamber-partitioning longitudinally extending baffle assembly 74 are positioned within the chamber 22 to effect a multi-pass, contraflow thermal exhange process, during operation, between the first and second fluids within the chamber 22 and the inner multi-walled tubes 75 thereby facilitating the transfer of heat therebetween.
  • neck flanges 44 and 46 are affixed to axially opposed ends of the shell 12 as by welding or an equivalent process.
  • the neck flanges 44, 46 are conveniently identical in structure, each including a port 20, 18 respectively and so forth, but are rotationally offset 72° from each other prior to affixation to the shell.
  • the assemblies 14, 16 respectively comprise a sandwich-like arrangement of elements joined to neck flanges 44 and 46 by a plurality of bolts 48 peripherally arranged about the assemblies 14 and 16 and threadedly engaged to nuts 50.
  • the inlet end assembly 14 includes an end cap 24, a center pressure flange 32 and an inner tube sheet 40.
  • a similar outlet end assembly arrangement comprises end cap 26, center pressure flange 34, and inner tube sheet 42.
  • the neck flange 44 conveniently includes exit port 20, through which the second heat transfer fluid exits, as well as a port 85 for pressure relief valve 86. Both ports communicate with interior chamber 22.
  • An axially-extending chamber-partitioning baffle assembly 74 located within the chamber 22, partitions the chamber into five axially-extending parts or sub-chambers. Each of the five partitioned regions encloses a defined nest of heat exchange multi-walled tubes 75.
  • Fig. 3 is an enlaged longitudinal partial section of the assembled end assembly 14 illustrating, in part, a representative of one of the heat exchange tubes.
  • Fig. 4 is an enlarged sectional view of a portion of expanded surface tubing taken about section line 5 in Fig. 3.
  • Fig 5 is a port section of the assembled end assembly 16 illustrating in part a representative of one of the heat exchange tubes.
  • the multi-walled tube 75 generally comprises an outer tube 96 and an inner tube 57 pressed together along a helical area of contact so that a gap or cavity 110 effectively spirals the length of the tube between adjacent spiral contact areas. If, for example, the outer tube 96 of the multi-walled tube 75 fractures, the second fluid will enter the spiral cavity 110 and, as subsequently described, such fracture will be detected by the venting of such fluid from within the cavity 110 to atmosphere. Similarly, when the inner tube 57 is breached, the first fluid will enter the spiral cavity 110 and will thereafter be vented to atmosphere.
  • multi-walled tube 75 has been designed to improve the heat transfer coefficient over conventional enhanced surface tubes. This improvement is achieved by providing a relatively wide groove where the outer tube 96 and the inner tube 57 are pressed together, yielding greater area of metal contact 122. Additionally, by increasing the distance 124 between the grooves to allow a thicker wetted surface to form, an increased heat transfer coefficient is provided. While it is known that enhanced surface tubing significantly increases the heat transfer of a particular tube diameter in heat exchange equipment, applicant has developed a particular configuration wherein the controlling parameters are optimized.
  • a groove width 122 of approximately 3,1 mm and depth of approximately 2,4 mm assures good turbulation of the fluids on both sides of the tube while maximizing heat transfer without collapsing the tube during manufacture.
  • the pitch 124 of the optimal tube is found to be 14,3 mm.
  • a gap 110 of 76 ⁇ m was employed to meet venting regulations but should be kept at a minimum to ensure maximum heat transfer.
  • the inner tube sheet 42 is first mounted onto the neck flange 46 by. means of locating dowels 70' protruding from the flange and receiving holes 38 in the tube sheet 42.
  • the dowels and dowel-receiving holes are similar to dowel 70 and holes 56 associated with tube sheet 40 of the inlet assembly and illustrated in Fig. 2.
  • the tube sheet 42 which is similar to plate 40 (Fig. 2) includes a pattern of holes sized to accomo- date the outer tubes 96 of the multi-walled tubes 75.
  • FIG. 5 a fragmentary sectional view of the outlet end of the heat exchanger 10.
  • Each of the multi-walled tubes 75 to be inserted into chamber 22 through a respective one of the holes in the innertube sheet 42, includes a bushing 104 which has been inserted over the end of the tube.
  • the bushing 104 includes a through-hole having a stopped wall 104a such that the larger internal diameter portion of the bushing engages the outer tube 96 of multi-walled tube 75, while the smaller diameter portion of the bushing engages the inner tube 57 of multi-walled tube 75.
  • a general swaging 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.
  • each bushing contacts a gasket similar to gasket 67 against the outer face of the plate 42.
  • the neck flange 44 is shown to include a number of peripheral apertures 33 and a longitudinally extending, peripheral dowel 70.
  • the dowel 70 is adapted to pass through location holes respectively formed in the components of end assembly 14 when the components are mounted onto the flange 44.
  • a gasket assembly comprising a tube sheet 40 interjacent two gaskets 68, 69 is mounted onto the flange 44.
  • the tube sheet 40 and gasket 68 include aligned hole patterns corresponding to the layout of tube holes 95 so that the multi-walled tubes 75 extend outward therethrough.
  • the gasket assembly and the corresponding gasket assembly of outlet assembly 16 define the ends of chamber 22 for the second heat transfer fluid.
  • each bushing 41 includes a pair of 0-rings 102, 103 for forming a tube expansion region 43 communicating with gap 110 in multi-walled tube 75.
  • a hole 111 which connects to gap 110 to allow the tube to vent to atmosphere.
  • gasket 67 is fitted over the protruding inner tube 57 of multi-walled tube 75.
  • a pressure flange 32 is then correctly orientated via dowel 70 and assembled onto the neck flange 44.
  • the axially inner face of pressure flange 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 the protruding bushings 41 and which is adapted to sealingly contact the gaskets 67 and 68 to define a vent chamber 45 between the flange 32 and tube sheet 40.
  • the vent passage is completed with a vent hole 47 in pressure flange annular portion 32a.
  • the aforedescribed arrangement is directed towards preventing the contamination of one of the heat exchange fluids by the other.
  • the fluid will enter region 43 pass through hole 111 then to atmosphere through hole 47.
  • the second fluid will not escape from gap 110 at the outlet assembly 16 since the expansion of multi-walled tube 75 into bushing 104 at that end has sealed that bushing across the gap.
  • 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 32a 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 pressure flange 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 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 gasket 67.
  • the inner tubes 57 extend into, but do not protrude from the axially outward side of passage 95.
  • the axially outer face of the pressure flange 32 includes an end baffle arrangement comprising annular portion 28a circumscribing the thorugh-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.
  • Assembly of the heat exchanger 10 is completed by positioning the end caps 24, 26 onto the neck flange 44, 46.
  • Bolts 48 are inserted through the apertures 33 in both neck flanges with their heads pointed towards the opposite end of 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 multi-walled tubes 75 may accordingly be inspected through apertures 95 without the voiding of the second fluid in chamber 22. This is particularly advantageous when the second fluid is a refrigerant.
  • the 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 0-rings 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 33, chamber 22, and the bushing 41 refitted to the replaced tube.
  • end assembly 16 (Fig. 5), it will be appreciated that any leakage of second heat transfer fluid through gaskets associated with the inner tube sheet 42 or the pressure flange 34 will be drawn into vent chamber 151 and vent to atmosphere by the same method as end assembly 14.
  • Another feature of the described embodiment is directed to the temperature-induced dimensional changes in the tubes 75.
  • higher outlet temperatures of the first fluid have been provided using a five segment chamber with successive counterflowing first and second fluids to increase surface contact time. Because the segments represent different temperature zones within the heat exchanger, the multi-walled tubes 75 of each segment will expand to a greater or lesser degree than the tubes of the remaining segments.
  • each multi-walled tube 75 to freely expand to the extent required, thereby meeting design codes governing such heat exchangers.
  • multi-walled tube 75 is permitted to "float" axially so that temperature-induced changes in standardized tube length may be accomodated during operation of the heat exchanger.
  • outer tube 96 of multi-walled tube 75 may slide axially within the 0-ring without loss of sealing contact therebetween.
  • inner tube 57 may slide axially within the 0-ring without loss of sealing contact between the two. Because tube 57 and tube 96 are joined together by metal contact area 122, multi-walled 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 the design specification of the ASME pressure vessel codes in the United States, as well as corresponding foreign codes.

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  • 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)

Claims (11)

1. Wärmetauscher mit
a) einem Paar von Endeinrichtungen (14, 16), die erste Einlaßmittell (54) und erste Auslaßmittel (62) zum jeweiligen Eintritt bzw. Austritt eines ersten Wärmetauscherfluids aufweisen,
b) einem im wesentlichen rohrförmigen Gehäuse (12), das sich zwischen dem Paar von Endeinrichtungen (14, 16) erstreckt, wobei die Endeinrichtungen (14, 16) an axial gegenüberliegenden Enden des Gehäuses angeordnet sind, um eine innerhalb des Gehäuses und zwischen den Endeinrichtungen (14, 16) liegende Innenkammer (22) zu bilden, und wobei das Gehäuse zweite Einlaßmittel (18) und zweite Auslaßmittel (20) zum jeweiligen Eintritt bzw. Austritt eines zweiten Wärmetauscherfluids aufweist,
c) einer Mehrzahl von Mehrwandrohren (75) mit Innen- und Außenrohren (57, 96), die axial innerhalb der Innenkammer (22) zwischen den Endeinrichtungen (14, 16) an jedem Ende verlaufen, wobei die Endeinrichtungen (14, 16) jeweils folgendes enthalten:
d) eine Rohrplatte (40, 42) mit einer Mehrzahl von axial verlaufenden Durchgangsöffnungen, von denen jede ein Außenrohr (96) eines anderen Mehrwandrohrs (75) aufnimmt, wobei die Rohrplatte (40, 42) mit einer in der Innenkammer (22) angeordneten Umlenkeinrichtung (74) zusammenarbeitet, um einen Strömungsweg für das zweite Fluid in der Innenkammer (22) zu bilden,
e) einen Mittenflansch (32, 34) an der der Innenkammer (22) abgewandten Seite der Rohrplatte (40, 42), wobei der Mittenflansch (32, 34) mit einer Mehrzahl von axialen Durchgangsöffnungen (95) versehen ist, von denen jede ein Innenrohr (57) eines anderen Mehrwandrohrs (75) aufnimmt, und
f) Endeinrichtungsmittel (24, 28; 26, 30) zum Einkoppeln des ersten Wärmetauscherfluids in die Innenrohre (57) wenigstens einer Mehrzahl von Mehrwandrohren (75),
g) wobei in wenigstens einer Endeinrichtung (14) der Mittenflansch (32) eine Entlüftungskammer (45) zwischen ihm und der Rohrplatte (40) definiert und die Entlüftungskammer (45) in Verbindung mit dem Raum zwischen dem Innenrohr (57) und dem Außenrohr (96) jedes Mehrwandrohres (75) steht, dadurch gekennzeichnet, daß
h) wenigstens in einer Endeinrichtung (14) von jedem Mehrwandrohr (75) das Außenrohr (96) von der Rohrplatte (40) und das Innenrohr (57) vom Mittenfiansch (32) getragen werden, und zwar so, daß eine axiale Verschiebung zwischen Außen- und Innenrohr möglich ist, und
i) Abdichtmittel (41, 67, 68, 102, 103; 104) mit einer Muffe (41, 104) zwischen der Rohrplatte (40, 42) und dem Mittenflansch (32, 34) zum Abdichten des Außenrohrs (96) und des Innenrohrs (57) eines jeden Mehrwandrohrs (75) bei axialer Bewegungsmöglichkeit relativ zur Muffe (41) sowie zum Abdichten der Muffe (41) gegenüber der Rohrplatte (40, 42) und dem Mittenflansch (32, 34) vorhanden sind, wobei jede Muffe (41, 104) mit einer Radialbohrung (111) versehen ist, um eine Verbindung zwischen dem Raum und der Entlüftungskammer (45) herzustellen.
2. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß die zwischen Rohrplatte (40, 42) und Mittenflansch (32, 34) angeordnete Muffe (41, 104) eine Innendurchgangsbohrung aufweist, deren Durchmesser an dem der Rohrplatte (40, 42) benachbarten Ende so gewählt ist, daß sie das Außenrohr (96) des Mehrwandrohrs (75) gleitend und abdichtend aufnimmt, und deren Durchmesser an dem dem Mittenflansch (32, 34) benachbarten Ende kleiner ist als der zuvor genannte Durchmesser und so gewählt ist, daß sie dort das Innenrohr (57) des Mehrwandrohrs (75) gleitend und abdichtend aufnimmt.
3. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Abdichtmittlel für jede Muffe (41, 104) eine erste Dichtung (103) enthalten, die gleitend den Bereich zwischen der Bohrung mit kleinerem Durchmesser und dem sie durchlaufenden Innenrohr (57) abdichtet, und eine zweite Dichtung (102) aufweisen, die gleitend den Bereich zwischen der Bohrung mit größerem Durchmesser und dem in sie hineinragenden Außenrohr (96) abdichtet.
4. Wärmetauscher nach Anspruch 3, dadurch gekennzeichnet, daß die erste und die zweite Dichtung (103, 102) O-Ring-Dichtungen sind.
5. Wärmetauscher nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, daß die Abdichtmittel Mittel (68) zum Abdichten jeder Muffe (41, 104) gegenüber der Rohrplatte (40, 42) an einem Ende benachbart zur Rohrplatte (40, 42) und Mittel (67) zum Abdichten jeder Muffe (41, 104) gegenüber dem Mittenflansch (32, 34) an einem Ende benachbart zum Mittenflansch (32, 34) enthalten.
6. Wärmetauscher nach Anspruch 2, 3 oder 4, gekennzeichnet durch Mittel (47) zur Bildung eines Fluidströmungswegs zwischen der Entlüftungskammer (45) und der Umgebung des Wärmetauschers (10), wobei die Radialbohrung (111) in jeder Muffe (41, 104) an einer Axialposition zwischen einem Übergang von der Bohrung mit größerem Durchmesser zur Bohrung mit kleinerem Durchmesser und dem Ende des Außenrohrs (96) liegt, das teilweise in die Bohrung mit größerem Durchmesser hineinragt.
7. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß durch das Paar von Endeinrichtungen (14, 16) die Innenkammer (22) als Zwischenbereich und ferner zwei Endbereiche (45, 151) definiert werden, die an gegenüberliegenden Seite des Zwischenbereichs liegen.
8. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Mehrwandrohre (75) jeweils ein Innenrohr (57) mit einer Wand gleichmäßiger Dicke und einer darin vorhandenen, spiralförmigen Furche sowie ein Außenrohr (96) aufweisen, das das Innenrohr (57) konzentrisch umgibt, und das eine Wand gleichmäßiger Dicke mit einer darin vorhandenen, spiralförmigen Furche besitzt, die zur spiralförmigen Furche im Innenrohr (57) paßt, derart, daß eine innere Oberfläche des Außenrohrs (96) mit einer äußeren Oberfläche des Innenrohrs (57) in Eingriff kommt, und zwar entlang der zueinander passenden Furchen von Innenrohr (57) und Außenrohr (96).
9. Wärmetauscher nach Anspruch 8, dadurch gekennzeichnet, daß Innen- und Außenrohr (57, 96) zwischen sich sowie zwischen benachbarten Spiralfurchen-Kontaktbereichen einen sich spiralförmig ausdehnenden Hohlraum (110) definieren, wobei die Spirale im Innenrohr (57) und im Außenrohr (96) eine Breite von etwa 3,1 mm, eine Tiefe von etwa 2,4 mm und eine Teilung von etwa 14,3 mm aufweist.
10. Wärmetauscher nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, daß die Endbereiche (45, 151) über die Mehrwandrohre (75) miteinander in Verbindung stehen.
11. Wärmetauscher nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, daß die Abdichtung an einem Ende der Mehrwandrohre (75) durch Ausdehnung der Wände der Mehrwandrohre (75) in der Bohrung der Muffe (104) sowie durch Dichtungen an beiden Seiten der Muffenwände und am anderen Ende durch Verwendung sich verjüngender Abdichtungen erzielt wird.
EP19870113723 1983-03-28 1984-03-27 Rohrbündelwärmetauscher Expired EP0259895B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US47923483A 1983-03-28 1983-03-28
US479234 1983-03-28
US58297584A 1984-02-23 1984-02-23
US582975 1984-02-23

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EP19840103378 Division-Into EP0120497B1 (de) 1983-03-28 1984-03-27 Gehäuse- und Röhrenwärmetauscher
EP84103378.0 Division 1984-03-27

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EP0259895A1 EP0259895A1 (de) 1988-03-16
EP0259895B1 true EP0259895B1 (de) 1990-07-18

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EP19840103378 Expired EP0120497B1 (de) 1983-03-28 1984-03-27 Gehäuse- und Röhrenwärmetauscher
EP19870113723 Expired EP0259895B1 (de) 1983-03-28 1984-03-27 Rohrbündelwärmetauscher

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CA (1) CA1264735A (de)
DE (2) DE3479153D1 (de)
DK (1) DK168684A (de)

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JPS63502847A (ja) * 1985-11-05 1988-10-20 テイ−ユ−アイ　インダストリ−ズ 胴と管型熱交換器
FR2603693B1 (fr) * 1986-09-05 1990-03-30 Toshiba Kk Echangeur de chaleur tubulaire a calandre
US4870734A (en) * 1987-04-03 1989-10-03 Tui Industries Method of manufacturing high efficiency heat exchange tube
US5004042A (en) * 1989-10-02 1991-04-02 Brunswick Corporation Closed loop cooling for a marine engine
DE3938254A1 (de) * 1989-11-17 1991-05-23 Behr Gmbh & Co Oelkuehler
EP0644394A1 (de) * 1993-09-21 1995-03-22 Proizvodstvennoe Obiedinenie "Chernovitsky Mashinostroitelny Zavod" Wärmeaustauscher
US10190765B2 (en) 2013-09-30 2019-01-29 Conleymax Inc. Heat exchanger
CN107449314B (zh) * 2017-07-24 2019-02-22 青岛德固特节能装备股份有限公司 一种金属套浮管密封结构
CN117470000B (zh) * 2023-12-26 2024-02-23 山东齐成石油化工有限公司 一种环保型石油化工用高效换热器

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Also Published As

Publication number Publication date
CA1264735A (en) 1990-01-23
EP0259895A1 (de) 1988-03-16
DK168684D0 (da) 1984-03-27
EP0120497A2 (de) 1984-10-03
EP0120497A3 (en) 1985-10-23
DK168684A (da) 1984-11-09
DE3482777D1 (de) 1990-08-23
EP0120497B1 (de) 1989-07-26
DE3479153D1 (en) 1989-08-31

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