EP3953654A1 - Stegdesign - und anordnung zur verringerung einer radialen fehlverteilung in einem gewickelten wärmeübertrager - Google Patents
Stegdesign - und anordnung zur verringerung einer radialen fehlverteilung in einem gewickelten wärmeübertragerInfo
- Publication number
- EP3953654A1 EP3953654A1 EP20719938.1A EP20719938A EP3953654A1 EP 3953654 A1 EP3953654 A1 EP 3953654A1 EP 20719938 A EP20719938 A EP 20719938A EP 3953654 A1 EP3953654 A1 EP 3953654A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tube bundle
- spacers
- tube
- 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.)
- Granted
Links
- 125000006850 spacer group Chemical group 0.000 claims abstract description 67
- 230000007423 decrease Effects 0.000 claims description 12
- 239000012530 fluid Substances 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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 the indirect heat transfer between a fluid first medium and at least one fluid second medium.
- Such a heat exchanger is e.g. used in natural gas liquefaction plants and has a shell space for receiving a first medium (refrigerant) and a plurality of tubes arranged in the shell space for receiving at least one second medium, which are wound around a core tube and a
- 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 outer side of the
- 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.
- the spacers reduce in a cross-sectional plane of the
- the calculated pressure drop in the shell space in the radial direction would not be constant, but greater inside than further outside. Since the flow through the column, however In reality, if the pressure loss is the same everywhere, the result is a higher flow velocity for the gaps further outside than for the gaps further inside and therefore a higher dynamic and lower static pressure component. This can then lead to a maldistribution of the phase of the first medium carried in the jacket space in the direction of the outer layers of the tube bundle in the jacket space.
- the present invention is therefore based on the problem of creating a heat exchanger of the type mentioned at the beginning which counteracts the above-mentioned maldistribution.
- 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 lies further out in the radial direction of the tube bundle, i.e. closer to the jacket than the first tube bundle gap.
- the individual tubes of the tube bundle are preferably wound helically on or around the core tube.
- the respective tube bundle gap is designed accordingly, in particular in the form of an annular gap.
- the core tube extends along a longitudinal axis of the jacket, the longitudinal axis in the case of a designated or intended use.
- heat exchanger arranged ready for operation is aligned vertically. Furthermore, according to one embodiment of the invention, it is provided that the thicknesses of those spacers which 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, the thickness of the spacers in the radial direction from the core tube to the jacket from the tube bundle gap
- Tube bundle gap decreases or remains the same. I.e. in particular that two or more tube bundle gaps that are adjacent in the radial direction can have spacers of the same thickness and only then does a decrease in thickness take place (at the transition to the next further outward tube bundle gap). I.e. the thickness does not necessarily have to decrease from tube bundle gap to tube bundle gap, but can also decrease in steps towards the outside.
- Tube bundle gap to tube bundle gap decreases.
- the thickness of the spacers decreases strictly monotonically towards the outside (in the radial direction).
- the spacers are designed as longitudinally extending webs which each extend 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 a width perpendicular thereto (in the circumferential direction of the tube bundle).
- the longitudinal direction of the respective spacer is parallel to the core tube or to the
- the longitudinal axis of the jacket / core tube runs.
- the respective spacer extends over an entire length of the tube bundle along the core tube or the longitudinal axis. Furthermore, it is provided according to one embodiment of the invention that the spacers in the respective tube bundle gap in the circumferential direction of the
- Tube bundle are arranged equidistant from one another.
- the spacers are grouped in such a way that a plurality of spacers for supporting the pipe layers are arranged one above the other in a radial direction of the pipe bundle.
- the number of spacers in the respective tube bundle gap is the same.
- Fig. 1 is a partially sectioned view of an embodiment of a
- Heat exchangers that have thicknesses decreasing in the radial direction
- FIG. 2 shows a schematic sectional view of a tube bundle of a heat exchanger according to the invention along a sectional plane which runs perpendicular to the longitudinal axis of the core tube according to FIG.
- 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, 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 guided in the tubes 10 of the tube bundle 15, so that it can enter into an indirect heat exchange with the first medium M guided in the shell space I.
- nozzles 3, 4 can be provided on the shell 2.
- the tube bundle 15 has a plurality of tubes 10, the tubes 10 each being wound at least in sections, preferably in a helical manner, around or onto a core tube 20 arranged in the shell space I, which extends along the
- Longitudinal axis Z extends so that a plurality of pipe 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
- the tubes 10 are for admitting at least one second medium M ‘into the
- At least one connector 6 is provided on the jacket 2 for drawing off the at least one medium M ‘from the tube bundle 15.
- the tube bundle 15 can also be used to introduce various second media M ‘in
- Figure 1 shows an example of three such tube groups.
- the tube bundle 15 can be surrounded by a cylindrical shirt 7 in order to suppress a bypass flow past the tube bundle 15.
- each spacer 30 is provided (cf. in particular FIG. 2), each of which is arranged in a tube bundle gap 200, 201, 202, 203, the respective Tube bundle gap 200, 201, 202, 203 is formed by two adjacent tube layers 100, 101; 101, 102, ... which extend in the radial direction R.
- Spacers 30 are provided so that the spacers 30 can be arranged one above the other in the radial direction R.
- the aforementioned constant number of spacers 30 per tube bundle gap 200, 201, 202, 203 has the consequence in the prior art that the relative reduction of a free cross-sectional area F of the respective
- Tube bundle gap 200, 201, 202, 203 due to 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 further out. Close to the core tube 20, this leads to a greater pressure drop on the shell space side in the tube bundle 15 than in areas or tube bundle gaps located further out in the radial direction R.
- the spacers 30 each have a thickness D in the radial direction R of the tube bundle 15, the thicknesses D of the spacers of a first tube bundle gap (e.g. 200 ) are each greater than the thickness of the spacers of a second tube bundle gap (eg 201) which lies further out in the radial direction R of the tube bundle 15, ie is closer to shell 2 than the first tube bundle gap (e.g. 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 jacket 2 decreases or remains the same from tube bundle gap to tube bundle gap. I.e. in particular that two or more tube bundle gaps adjacent in the radial direction R can have spacers 30 of the same thickness and only then is there a decrease in thickness D, so that there is a stepped decrease in thicknesses D towards the outside.
- Tube bundle gap 200, 201; 201, 202; 202, 203 decreases.
- the spacers 30 are preferably designed as elongated webs 30 (cf. FIG. 1), each of which extends 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 is 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 an entire length of the tube bundle 15 along the core tube 20.
- the spacers 30 are preferably arranged equidistant 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 out (e.g. 202, 203) can be reduced or to the free
- Cross-sectional areas F of the further inner tube bundle gaps are matched, which counteracts the jacket-side maldistribution of the first medium or the refrigerant.
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
Description
Claims
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 (de) | 2019-04-12 | 2020-03-31 | Stegdesign - und anordnung zur verringerung einer radialen fehlverteilung in einem gewickelten wärmeübertrager |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3953654A1 true EP3953654A1 (de) | 2022-02-16 |
EP3953654B1 EP3953654B1 (de) | 2023-04-26 |
Family
ID=70295081
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20719938.1A Active EP3953654B1 (de) | 2019-04-12 | 2020-03-31 | Stegdesign - und anordnung zur verringerung einer radialen fehlverteilung in einem gewickelten wärmeübertrager |
Country Status (4)
Country | Link |
---|---|
US (1) | US20220196331A1 (de) |
EP (1) | EP3953654B1 (de) |
DE (1) | DE102019002704A1 (de) |
WO (1) | WO2020207626A1 (de) |
Families Citing this family (1)
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)
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 |
DE60207689T3 (de) * | 2002-05-27 | 2013-01-24 | Air Products And Chemicals, Inc. | Wärmetauscher mit gewickelten Rohrschlangen |
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 (de) * | 2016-06-21 | 2017-12-28 | Linde Aktiengesellschaft | Gewickelter wärmeübertrager mit dummy-rohrlage zwischen kernrohr und innerster rohrlage |
WO2017220210A1 (de) * | 2016-06-21 | 2017-12-28 | Linde Aktiengesellschaft | Definition der vorspannung der rohre beim wickeln eines rohrbündels eines gewickelten wärmeübertragers |
-
2019
- 2019-04-12 DE DE102019002704.3A patent/DE102019002704A1/de not_active Withdrawn
-
2020
- 2020-03-31 EP EP20719938.1A patent/EP3953654B1/de active Active
- 2020-03-31 WO PCT/EP2020/025151 patent/WO2020207626A1/de unknown
- 2020-03-31 US US17/594,200 patent/US20220196331A1/en active Pending
Also Published As
Publication number | Publication date |
---|---|
WO2020207626A1 (de) | 2020-10-15 |
DE102019002704A1 (de) | 2020-10-15 |
US20220196331A1 (en) | 2022-06-23 |
EP3953654B1 (de) | 2023-04-26 |
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