EP3953654B1 - Conception et arrangement de support des tubes d'un échangeur de chaleur enroulé pour éviter une maldistribution radial - Google Patents

Conception et arrangement de support des tubes d'un échangeur de chaleur enroulé pour éviter une maldistribution radial Download PDF

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Publication number
EP3953654B1
EP3953654B1 EP20719938.1A EP20719938A EP3953654B1 EP 3953654 B1 EP3953654 B1 EP 3953654B1 EP 20719938 A EP20719938 A EP 20719938A EP 3953654 B1 EP3953654 B1 EP 3953654B1
Authority
EP
European Patent Office
Prior art keywords
tube bundle
tube
spacers
heat exchanger
gap
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.)
Active
Application number
EP20719938.1A
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German (de)
English (en)
Other versions
EP3953654A1 (fr
Inventor
Manfred Steinbauer
Jürgen Spreemann
Florian Deichsel
Konrad Braun
Manuel KNAUP
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.)
Linde GmbH
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Linde GmbH
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Publication date
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Publication of EP3953654A1 publication Critical patent/EP3953654A1/fr
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Publication of EP3953654B1 publication Critical patent/EP3953654B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—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 helically coiled
    • F28D7/022—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 helically coiled the conduits of two or more media in heat-exchange relationship being helically coiled, the coils having a cylindrical configuration
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • the invention relates to a heat exchanger for indirect heat transfer between a first fluid medium and at least one second fluid medium.
  • Such a heat exchanger is used, for example, in natural gas liquefaction plants and has a jacket space for holding a first medium (refrigerant) and a plurality of tubes arranged in the jacket space for holding at least one second medium, which are wound around a core tube and a tube bundle with several tubes lying one above the other form pipe layers.
  • the tube bundle has a plurality of spacers for supporting or mechanically stabilizing the tube layers, which are each arranged in a tube bundle gap between two adjacent tube layers or in particular also in an innermost tube bundle gap between an innermost tube layer and an outside of the core tube.
  • the number of spacers per tube bundle gap is usually constant, so that the spacers for supporting the tube layers can be arranged one above the other in the radial direction of the tube bundle. In this way, the weight of all pipe layers can be supported by the spacers without damaging the pipes of individual pipe layers.
  • Heat exchangers according to the preamble of claim 1 are from documents U.S. 2010/096115 A1 and DE 26 13 745 A1 known.
  • the spacers reduce the free cross-sectional area of the shell space between the tube layers in a cross-sectional plane of the shell space perpendicular to the longitudinal axis (vertical) of the core tube or tube bundle, so that due to the constant number of spacers per tube bundle gap (see above) the free cross-sectional areas between experience a greater relative reduction in the inner tube layers or in the inner tube bundle gaps than the free cross-sectional areas of the tube bundle gaps further out.
  • the calculated pressure drop in the jacket space would not be constant in the radial direction, but would be greater inside than further outside.
  • the present invention is therefore based on the problem of creating a heat exchanger of the type mentioned at the outset, which counteracts the above-mentioned maldistribution.
  • the spacers each have a thickness in the radial direction of the tube bundle, the thicknesses of the spacers of a first tube bundle gap being greater than the thicknesses of the spacers of a second tube bundle gap, which is further outward in the radial direction of the tube bundle, i.e. closer to the shell than the first tube bundle gap.
  • the individual tubes of the tube bundle are preferably wound helically onto or around the core tube.
  • the respective tube bundle gap is correspondingly designed in particular in the form of an annular gap.
  • the thicknesses of those spacers that are arranged in the same tube bundle gap are of the same size.
  • the spacers have more than two, in particular three to four, different thicknesses in the radial direction of the tube bundle, with the thickness of the spacers decreasing in the radial direction from the core tube to the shell from tube bundle gap to tube bundle gap or remains the same.
  • two or more tube bundle gaps that are adjacent in the radial direction can have spacers of the same thickness and only then does the thickness decrease (at the transition to the next tube bundle gap that is further out).
  • the thickness does not necessarily have to decrease from tube bundle gap to tube bundle gap, but can also decrease outwards in a step-like manner.
  • the thickness of the spacers decreases in the radial direction from the core tube to the shell from tube bundle gap to tube bundle gap. In this case, the thickness of the spacers decreases in a strictly monotonous manner towards the outside (in the radial direction).
  • the spacers are designed as elongate webs, each of which extends in a longitudinal direction.
  • the spacers or webs can have a rectangular cross-section perpendicular to the longitudinal direction, which has the said thickness and has a width perpendicular thereto (in the circumferential direction of the tube bundle).
  • the longitudinal direction of the respective spacer runs parallel to the core tube or to the longitudinal axis of the casing/core tube.
  • the respective spacer extends over an entire length of the tube bundle along the core tube or the longitudinal axis.
  • the spacers are arranged equidistantly from one another in the respective tube bundle gap in the circumferential direction of the tube bundle.
  • the spacers are grouped in such a way that a plurality of spacers for supporting the tube layers are arranged one above the other in a radial direction of the tube bundle.
  • the number of spacers in the respective tube bundle gap is the same.
  • FIG 1 shows an embodiment of a heat exchanger 1 according to the invention.
  • This has a jacket 2 which encloses a jacket space I of the heat exchanger 1 .
  • a tube bundle 15 is arranged in the shell space I, which is acted upon along the longitudinal axis Z of the heat exchanger 1 or shell 2 with a liquid phase of a first medium M, which is, for example, a refrigerant.
  • At least one second fluid medium M′ is conducted in the tubes 10 of the tube bundle 15 so that it can enter into an indirect heat exchange with the first medium M conducted in the shell space I.
  • To admit the first Medium M in the shell space I or for withdrawing the first medium M from the shell space I can be provided on the shell 2 sockets 3, 4.
  • the tube bundle 15 has a plurality of tubes 10, with the tubes 10 each being wound at least in sections, preferably helically, around or onto a core tube 20 which is arranged in the shell space I and extends along the longitudinal axis Z, so that a plurality of tube layers 101, 102, 103, 104 are formed, which lie one above the other in the radial direction R of the tube bundle 15 or of the core tube 20.
  • the respective radial direction R is perpendicular to the longitudinal axis Z and points outwards from the longitudinal axis Z toward the jacket 2 .
  • the tubes 10 are flow-connected to at least one connector 5 provided on the jacket 2 for admitting at least one second medium M ⁇ into the tube bundle 15 .
  • the tube bundle 15 can also be divided into tube groups for the introduction of various second media M ⁇ , each of which has an associated inlet or connection piece 5 and an outlet or connection piece 6 .
  • the figure 1 shows three such tube groups as an example.
  • the tube bundle 15 can be surrounded by a cylindrical shirt 7 in order to suppress a bypass flow past the tube bundle 15 .
  • a plurality of spacers 30 are provided for the mechanical stabilization of the tube bundle 15 or the individual tube layers 100, 101, 102, 103 (cf. in particular figure 2 ). , wherein the innermost tube bundle gap 200 lies between an outer side 20a of the core tube 20 and the innermost layer 100 of tubes.
  • the spacers 30 can support the weight of the individual tube layers 100 , 101 , 102 , 103 via the spacers 30 .
  • a constant number of spacers 30 are therefore preferably provided in each tube bundle gap 200, 201, 202, 203, so that the spacers 30 can be arranged one above the other in the radial direction R.
  • the said constant number of spacers 30 per tube bundle gap 200, 201, 202, 203 has the consequence that the relative reduction of a free cross-sectional area F of the respective tube bundle gap 200, 201, 202, 203 oriented transversely to the longitudinal axis Z by the spacers 30 arranged one above the other in the radial direction R is greater closer to the core tube 20 than in the case of tube bundle gaps located further outward.
  • the invention provides (cf. figure 2 ) that the spacers 30 each have a thickness D in the radial direction R of the tube bundle 15, with the thicknesses D of the spacers of a first tube bundle gap (e.g. 200) each being greater than the thicknesses of the spacers of a second tube bundle gap (e.g. 201) which in radial direction R of the tube bundle 15 is further outside, that is closer to the shell 2 than the first tube bundle gap (eg 200).
  • the thicknesses of the spacers 30 are preferably the same.
  • the spacers 30 have more than two, in particular three to four, different thicknesses D in the radial direction R of the tube bundle 15, the thickness D of the spacers 30 in the radial direction R from the core tube 20 to the shell 2 decreases from tube bundle gap to tube bundle gap or remains the same.
  • two or more tube bundle columns adjacent in the radial direction R can have spacers 30 of the same thickness and only then does the thickness D decrease, so that the thicknesses D decrease in stages towards the outside.
  • the thickness D of the spacers 30 in the radial direction from the core tube 20 to the jacket 2 from tube bundle gap to tube bundle gap 200, 201; 201, 202; 202, 203 decreases.
  • the spacers 30 are preferably designed as elongate webs 30 (cf. 1 ), each extending in a longitudinal direction.
  • the spacers 30 or webs can have a rectangular cross section perpendicular to the longitudinal direction. It is preferably provided that the longitudinal direction of the respective spacer runs parallel to the core tube 20 or parallel to the longitudinal axis Z runs. Furthermore, it is preferably provided that the respective spacer 30 extends over the entire length of the tube bundle 15 along the core tube 20 .
  • the spacers 30 are preferably arranged equidistantly from one another in the respective tube bundle gap 200, 201, 202, 203.
  • the free cross-sectional area F of the tube bundle gaps located further outside can be reduced or adapted to the free cross-sectional areas F of the tube bundle gaps located further inside (e.g. 200, 201) must be adjusted, which counteracts the maldistribution of the first medium or the refrigerant on the shell side.

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

Claims (12)

  1. Échangeur de chaleur (1) pour le transfert de chaleur indirect entre un premier et au moins un second milieu (M, M'), comportant
    - un espace d'enveloppe (I) pour la réception du premier milieu (M),
    - un tube central (20) disposé dans l'espace d'enveloppe (I),
    - un faisceau de tubes (15) disposé dans l'espace d'enveloppe (I) et présentant plusieurs tubes (10) respectivement enroulés autour du tube central (20), de sorte que le faisceau de tubes (15) présente plusieurs couches de tube (100, 101, 102, 103) superposées, lesquelles présentent respectivement au moins un tube (10), une fente de faisceau de tubes (200, 201, 202, 203) étant prévue entre respectivement deux couches de tube (100, 101 ; 101, 102 ;...) adjacentes, plusieurs entretoises (30) permettant de supporter les couches de tube (100, 101, 102, 103) étant disposées dans chaque fente de faisceau de tubes (200, 201, 202, 203),
    caractérisé en ce
    que les entretoises (30) présentent respectivement une épaisseur (D) dans la direction radiale (R) du faisceau de tubes (15), les épaisseurs (D) des entretoises (30) d'une première fente de faisceau de tubes (200) étant respectivement supérieures aux épaisseurs (D) des entretoises d'une seconde fente de faisceau de tubes (203), laquelle, dans la direction radiale (R) du faisceau de tubes (15), se trouvant plus à l'extérieur que la première fente de faisceau de tubes (200).
  2. Échangeur de chaleur selon la revendication 1, caractérisé en ce que les épaisseurs (D) des entretoises (30) disposées dans la même fente de faisceau de tubes (200, 201, 202, 203) sont égales.
  3. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que les entretoises (30) présentent plus de deux, en particulier trois à quatre, épaisseurs (D) différentes, l'épaisseur (D) des entretoises, dans la direction radiale (R), diminuant ou restant la même de fente de faisceau de tubes à fente de faisceau de tubes, du tube central (20) vers l'enveloppe (2).
  4. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que l'épaisseur (D) des entretoises (30), dans la direction radiale (R), diminue de fente de faisceau de tubes à fente de faisceau de tubes, du tube central (20) vers l'enveloppe (2).
  5. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que les entretoises (30) sont réalisées en tant que nervures (30) s'étendant longitudinalement, lesquelles s'étendent respectivement dans une direction longitudinale.
  6. Échangeur de chaleur selon la revendication 5, caractérisé en ce que la direction longitudinale de l'entretoise (30) respective s'étend parallèlement au tube central (20).
  7. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que l'entretoise (30) respective s'étend au moins sur toute une longueur du faisceau de tubes (15) le long du tube central (20).
  8. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que les entretoises (30) sont disposées de manière équidistante les unes par rapport aux autres dans la fente de faisceau de tubes (200, 201, 202, 203) respective dans la direction circonférentielle (U) du faisceau de tubes (15).
  9. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce qu'une fente de faisceau de tubes la plus intérieure (200), dans laquelle sont disposées plusieurs entretoises (30), est prévue entre une couche de tube la plus intérieure (100) dans la direction radiale (R) du faisceau de tubes (15) et une face extérieure (20a) du tube central (20).
  10. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que les entretoises (30) sont groupées de telle sorte que respectivement plusieurs entretoises (30) permettant de supporter les couches de tube (100, 101, 102, 103) sont superposées dans une direction radiale (R) du faisceau de tubes (15).
  11. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que le nombre d'entretoises (30) dans la fente de faisceau de tubes (200, 201, 202, 203) respective est le même.
  12. Échangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que le nombre d'entretoises (30) dans au moins deux fentes de faisceau de tubes est différent.
EP20719938.1A 2019-04-12 2020-03-31 Conception et arrangement de support des tubes d'un échangeur de chaleur enroulé pour éviter une maldistribution radial Active EP3953654B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019002704.3A DE102019002704A1 (de) 2019-04-12 2019-04-12 Stegdesign - und Anordnung zur Verringerung einer radialen Fehlverteilung in einem gewickelten Wärmeübertrager
PCT/EP2020/025151 WO2020207626A1 (fr) 2019-04-12 2020-03-31 Conception d'entretoise et ensemble formant entretoise servant à réduire une répartition erronée radiale dans un échangeur de chaleur enroulé

Publications (2)

Publication Number Publication Date
EP3953654A1 EP3953654A1 (fr) 2022-02-16
EP3953654B1 true EP3953654B1 (fr) 2023-04-26

Family

ID=70295081

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20719938.1A Active EP3953654B1 (fr) 2019-04-12 2020-03-31 Conception et arrangement de support des tubes d'un échangeur de chaleur enroulé pour éviter une maldistribution radial

Country Status (4)

Country Link
US (1) US20220196331A1 (fr)
EP (1) EP3953654B1 (fr)
DE (1) DE102019002704A1 (fr)
WO (1) WO2020207626A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11561049B2 (en) * 2020-05-05 2023-01-24 Air Products And Chemicals, Inc. Coil wound heat exchanger

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB912710A (en) * 1959-02-04 1962-12-12 Superheater Co Ltd Improvements in steam raising systems
GB1201855A (en) * 1968-07-31 1970-08-12 Babcock & Wilcox Ltd Improvements in or relating to tubular heat exchangers
DE2613745A1 (de) * 1976-03-31 1977-10-06 Linde Ag Waermetauscher
EP1367350B2 (fr) * 2002-05-27 2012-10-24 Air Products And Chemicals, Inc. Echangeur de chaleur avec serpentins de tubes
GB2463482B (en) * 2008-09-12 2012-05-02 Tanjung Citech Uk Ltd A heat exchange unit
US20100096115A1 (en) * 2008-10-07 2010-04-22 Donald Charles Erickson Multiple concentric cylindrical co-coiled heat exchanger
DE102016005838A1 (de) * 2016-05-12 2017-11-16 Linde Aktiengesellschaft Gewickelter Wärmeübertrager mit Einbauten zwischen Hemd und letzter Rohrlage
WO2017220209A1 (fr) * 2016-06-21 2017-12-28 Linde Aktiengesellschaft Échangeur de chaleur spiralé muni d'une couche de tubes factice entre le tube central et la couche de tubes la plus à l'intérieur
WO2017220210A1 (fr) * 2016-06-21 2017-12-28 Linde Aktiengesellschaft Définition de la précontrainte de tubes lors de l'enroulement d'un faisceau de tubes d'un échangeur de chaleur à spirales

Also Published As

Publication number Publication date
EP3953654A1 (fr) 2022-02-16
US20220196331A1 (en) 2022-06-23
DE102019002704A1 (de) 2020-10-15
WO2020207626A1 (fr) 2020-10-15

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