EP0031919A1 - Echangeur de chaleur tubulaire à espace annulaire - Google Patents

Echangeur de chaleur tubulaire à espace annulaire Download PDF

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Publication number
EP0031919A1
EP0031919A1 EP80107819A EP80107819A EP0031919A1 EP 0031919 A1 EP0031919 A1 EP 0031919A1 EP 80107819 A EP80107819 A EP 80107819A EP 80107819 A EP80107819 A EP 80107819A EP 0031919 A1 EP0031919 A1 EP 0031919A1
Authority
EP
European Patent Office
Prior art keywords
tubes
heat exchanger
segment
displacement
tube bundle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP80107819A
Other languages
German (de)
English (en)
Inventor
Günter Heck
Erhard Dr. Muthmann
Rudolf Rossmeissl
Heinz Schmidt
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.)
Hoechst AG
Original Assignee
Hoechst AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6089144&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0031919(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hoechst AG filed Critical Hoechst AG
Publication of EP0031919A1 publication Critical patent/EP0031919A1/fr
Ceased legal-status Critical Current

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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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/12—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 one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits

Definitions

  • the invention relates to a heat exchanger with a greatly increased heat transfer area by using the annular gap principle.
  • annular gap tube heat exchanger in which filler rods are arranged as displacers in the exchanger tubes, so that there are annular gaps between the inner walls of the exchanger tubes and the displacers, in which the medium to be cooled or heated (primary medium) flows (cf. FR-PS 12 49 001).
  • primary medium cf. FR-PS 12 49 001
  • the annular gap principle in this form can only be used with small heat exchangers. With large heat exchangers, the displacers become too heavy and unwieldy with large dimensions.
  • the task was therefore to find a heat exchanger that allows intensive heat exchange with large dimensions.
  • the invention relates to the heat exchanger mentioned in the claims.
  • the heat exchanger according to the invention consists of a cylindrical part, which is formed from several segments, and two hoods closing this part.
  • the largest of these segments consists of a cylinder, which is closed on two sides by flat, circular bottoms.
  • a number of parallel tubes are arranged between the two trays. They are largely pressure-tightly fastened in the floors, for example by rolling in or welding in.
  • the number of these outer tubes is 1 to approx. 3000, preferably 1 to 1500, they are preferably distributed symmetrically over the cross section of the segment. They are approx. 100 to approx. 8000 mm, preferably 1000 to 6000 mm long, have a diameter of approx. 15 to approx. 150 mm, preferably 30 to 100 mm, and a wall thickness of approx. 1 to approx. 10 mm, preferably 2 to 6 mm.
  • connectors are provided for the inflow or outflow of the heating or cooling medium.
  • a displacer body projects into each outer tube of the large heat exchanger segment such that a narrow, annular gap of approximately 1 to approximately 20 mm, preferably 2 to 10 mm, is formed between the inner wall of the respective outer tube and the displacer body.
  • the displacers can have suitable spacers, e.g. cams, ribs or the like. wear so that they keep the same distance from the inner walls of the outer tubes of the large segment.
  • the displacers can also have a cross-section and a shape which cause the displacers to touch the outer tubes from time to time and generally maintain a distance.
  • the displacement themselves consist of tubes with a diameter of about 10 mm to about 140, preferably from 20 mm to 80, a length of about 10 0 mm to about 8000, preferably 1000 to 6000 mm and a wall thickness of about 1 up to approx. 10 mm, preferably 2 to 6 mm.
  • the displacement tubes are also attached to a flat floor. This floor is at a distance corresponding to the height of a small heat exchanger segment from the nearest floor of the large heat exchanger segment.
  • the displacer tubes may be open, in which case they will be loosened in a second flat floor, e.g. held by glands. This floor is in turn. at a distance corresponding to the height of a small heat exchanger segment from the next bottom of the large heat exchanger segment, so that a chamber is also formed.
  • the displacement tubes can also be closed on one side. In this case, they must be wide enough to allow the heating or cooling medium to flow back and forth.
  • the heating or cooling medium is preferably brought to the closed end of the displacement tubes by means of inner tubes which are introduced into the displacement tubes, so that it flows back in the gap between the displacement tubes and the inner tubes. If condensate forms, its removal is supported by the steam flowing in.
  • inner tubes also have a diameter of approximately 6 to approximately 130 mm, preferably approximately 14 to 70 mm, a length of approximately 100 to approximately 8000 mm, preferably 1000 to 6000 mm, and a wall thickness of approximately
  • 1 to approx. 10 mm, preferably 2 to 6 mm, are fastened in a flat base, which is separated from the base carrying the displacement tubes by a small heat exchanger segment.
  • the large heat exchanger segment is approx. 100 to approx. 8000 mm, preferably 1000 to 6000 mm long and has a diameter of the cylinder wall (without flanges and sockets) of approx. 25 to approx. 3000 mm, preferably 150 to 1600 mm, the wall thickness depends on the operating pressure and material and is preferably approx. 2 to 60 mm.
  • baffles are expediently installed in the large segment in order to distribute the heating or cooling medium more evenly over the to be able to distribute the whole room.
  • the small segments have a height of about 100 mm to about 2000, preferably 200 to 600 mm, their diameters are the same as the large segment, their wall thicknesses can in the case of F ert Trentsvorieri be equal. All small segments are preferably the same in their dimensions and have the same number of connecting pieces, so that the cylindrical part of the heat exchanger can only consist of two different types of segments.
  • the connecting pieces can also be the same size, but preferably the inlet pieces for the heating medium are larger than the other pieces.
  • the displacement tubes and possibly the inner tubes with them are not of the same length, but have different lengths. These measures simplify and facilitate assembly and disassembly.
  • a spacer for the displacer and / or inner tubes can be inserted in the corresponding segments to make threading even easier (movable plate with the same pitch as the tube plate).
  • the hoods are commercially available boiler hoods and can be obtained from stock in all desired sizes.
  • the entire heat exchanger is preferably made of metal, for example, depending on the aggressiveness of the media, from boiler plate or stainless steel. However, it is also possible to make it out of glass or graphite.
  • the figures show examples of the heat exchanger according to the invention as it is operated as an evaporator / condenser in a vertical or inclined position.
  • the heat exchanger according to Figure 1 consists of the large cylindrical segment (1), the small cylindrical segments (2) and the hoods (3).
  • the outer tubes (6) are also welded to the flat floors (4) and (5) welded in the segment (1). Steam flows through the nozzle (7) into the segment (1) and flows around the pipes (6), while the condensate leaves the segment (1) through the nozzle (8).
  • In the tubes (6) there are displacement tubes (9) with spacers (9a), which are welded into the base (10) and are movably guided in a gland (11a) in the base (11).
  • the bottoms (10) and (11) are loosely between the flanges (12) of the segments (2) and the hoods (3) and are held in place when these flanges are screwed together.
  • the product to be heated passes through the nozzle (13) into the heat exchanger, flows upwards in the annular gap between the pipes (6) and (9) and leaves the apparatus through the nozzle (14). Steam flows through the nozzle (15) in the upper hood (3) through the displacement tubes (9), the condensate leaves the heat exchanger through the nozzle (16) in the lower hood (3). In this way, the product to be heated is from two sides heated.
  • the heat exchanger according to FIG. 3 also consists of the large segment (1), the small segments (2), the hoods (3), the bottoms (4) and (5) welded into the segment (1) with the tubes (6) and the nozzle (7) and (8).
  • Connecting piece (7) is used for steam inlet
  • connection piece (8) ondensatabgang the K.
  • the displacement tubes (9) welded into the base (10), which is held between the segments (2) by means of the flanges (12), are of different lengths and are closed at the end opposite the base (10).
  • Heating steam enters the heat exchanger through the connector (14), flows up into the displacement pipes (9) and condenses there, while the condensate flows out through the connector (16).
  • the product to be heated flows through the nozzle (13), through the annular gap between the tubes (6) and (9) and through the nozzle (15) again.
  • FIG. 4 A heat exchanger, with which particularly clear flow conditions can be achieved with permanently welded pipes, is shown in FIG. 4. It consists of the segments (1) and (2) with the hoods (3).
  • the segment (1) contains the pipes (6) permanently installed in the bottoms (4) and (5), this segment also contains the nozzle (7) for the steam inlet and the nozzle (8) for the condensate drain.
  • the displacement tubes (9) are of unequal length and are welded into the base (10), which is located between the two segments (2) below the segment (1). Inside the displacement tubes (9), which are closed on one side, there are inner tubes (17) with spacers (17a) which are welded into the flat bottom (18). This bottom is by means of the lower hood (3) the flanges (12) held.
  • the product to be heated enters the heat exchanger through the connector (13) and flows through the annular gap between the outer tubes (6) and the displacement tubes (9) and leaves the apparatus through the connector (15). Further steam enters through the nozzle (16), flows up in the inner tubes (17) and back in the annular gap between the inner tubes (17) and the displacement tubes (9) with condensation and emerges again through the nozzle (19).
  • FIG 5 shows the arrangement of the tubes (6), the displacement tubes (9) and the inner tubes (17) in the segment (1).
  • the steam is introduced into the heat exchanger according to the invention in two places. Part of the steam flows around the large installed pipes and condenses on them. The other part of the steam flows through the displacement pipes in order to condense there.
  • This type of steam routing causes the product flow in the annular gap between the fixed tubes in the large segment and the displacement tubes to absorb condensation heat from two sides.
  • the displacement pipes ensure that the same heat transfer coefficients as for normal pipes (empty pipes) are achieved with lower product quantities.
  • the displacement tubes achieve a significantly higher heat transfer area, which depends on the ratio of the diameter of the outer tube (6) and the displacement tube (9) to one another. Special flow forms (e.g. tangential flow, turbulent flow etc.) can be achieved by means of installations (9a) in the annular gap between the pipes (6) and (9).
  • the heat exchanger according to the invention can be operated as an evaporator / condenser in a vertical or inclined position.
  • the position is arbitrary for heat exchange without phase change.

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)
EP80107819A 1979-12-21 1980-12-11 Echangeur de chaleur tubulaire à espace annulaire Ceased EP0031919A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2951549 1979-12-21
DE19792951549 DE2951549A1 (de) 1979-12-21 1979-12-21 Ringspalt-rohrbuendel-waermetauscher

Publications (1)

Publication Number Publication Date
EP0031919A1 true EP0031919A1 (fr) 1981-07-15

Family

ID=6089144

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80107819A Ceased EP0031919A1 (fr) 1979-12-21 1980-12-11 Echangeur de chaleur tubulaire à espace annulaire

Country Status (3)

Country Link
EP (1) EP0031919A1 (fr)
JP (1) JPS5697790A (fr)
DE (1) DE2951549A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0107066A1 (fr) * 1982-10-18 1984-05-02 Anton Steinecker Maschinenfabrik GmbH Echangeur de chaleur à tubes doubles
EP0348299A1 (fr) * 1988-06-22 1989-12-27 Innovations Thermiques Echangeur de chaleur
FR2641067A1 (fr) * 1988-12-22 1990-06-29 Didier Werke Ag
EP1189007A2 (fr) * 2000-09-19 2002-03-20 Piero Pasqualini Echangeur de chaleur
WO2003073031A1 (fr) * 2002-02-26 2003-09-04 Wärtsilä Finland Oy Systeme d'echangeur thermique et procede utilise dans un echangeur thermique
CN101446474B (zh) * 2008-12-25 2010-04-07 化学工业第二设计院宁波工程有限公司 套管组合式防堵塞原油换热器
CN104930883A (zh) * 2015-06-25 2015-09-23 李铭珏 一种高效热交换器
BE1022816B1 (nl) * 2015-09-03 2016-09-13 Smo Bvba Warmtewisselaar en werkwijze voor het genereren van stoom
CN109029023A (zh) * 2017-06-08 2018-12-18 深圳市龙澄高科技环保（集团）有限公司 一种新型集合多套管快速拆装换热器

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59173688A (ja) * 1983-03-18 1984-10-01 ザ・ダウ・ケミカル・カンパニ− 熱交換器およびその操作法
JPS60196499A (ja) * 1984-03-21 1985-10-04 Shinmikuni Kikai Seisakusho:Kk 液化石油ガスの気化装置
DE3618295A1 (de) * 1986-05-30 1987-12-03 Wilfried Dipl Ing Buttchereit Waermetauscher
FI88203C (fi) * 1989-04-26 1993-04-13 Kalervo Paeivioe Maekinen Anordning foer oeverfoering av vaerme
DE4228923C2 (de) * 1992-08-30 1994-07-14 Sladky Hans Vorrichtung zur Kühlung von Flüssigkeiten
DE29716465U1 (de) * 1997-09-16 1998-02-26 Gehring, Wolfgang, 97725 Elfershausen Doppelrohrmehrkreiskühler für Brennereien (Gegenstrom oder Gleichstrom) z.B. (1 Medienkreislauf) (2 Kühlkreisläufe)
DE10030627A1 (de) * 2000-06-28 2002-01-17 Ultrafilter Internat Ag Wärmetauscher für Kältetrockneranlagen
DE202005017583U1 (de) * 2005-11-10 2007-03-22 Dietz, Erwin Wärmeübertrager

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB260066A (en) * 1925-08-12 1926-10-28 Emilio Storoni Heat exchange apparatus

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB260066A (en) * 1925-08-12 1926-10-28 Emilio Storoni Heat exchange apparatus

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0107066A1 (fr) * 1982-10-18 1984-05-02 Anton Steinecker Maschinenfabrik GmbH Echangeur de chaleur à tubes doubles
EP0348299A1 (fr) * 1988-06-22 1989-12-27 Innovations Thermiques Echangeur de chaleur
FR2633378A1 (fr) * 1988-06-22 1989-12-29 Innovations Thermiques Echangeur de chaleur a deux flux
FR2641067A1 (fr) * 1988-12-22 1990-06-29 Didier Werke Ag
EP1189007A2 (fr) * 2000-09-19 2002-03-20 Piero Pasqualini Echangeur de chaleur
EP1189007A3 (fr) * 2000-09-19 2005-02-09 Piero Pasqualini Echangeur de chaleur
WO2003073031A1 (fr) * 2002-02-26 2003-09-04 Wärtsilä Finland Oy Systeme d'echangeur thermique et procede utilise dans un echangeur thermique
CN101446474B (zh) * 2008-12-25 2010-04-07 化学工业第二设计院宁波工程有限公司 套管组合式防堵塞原油换热器
CN104930883A (zh) * 2015-06-25 2015-09-23 李铭珏 一种高效热交换器
BE1022816B1 (nl) * 2015-09-03 2016-09-13 Smo Bvba Warmtewisselaar en werkwijze voor het genereren van stoom
CN109029023A (zh) * 2017-06-08 2018-12-18 深圳市龙澄高科技环保（集团）有限公司 一种新型集合多套管快速拆装换热器

Also Published As

Publication number Publication date
DE2951549A1 (de) 1981-07-02
JPS5697790A (en) 1981-08-06

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Effective date: 19811003

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Effective date: 19840413

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Inventor name: SCHMIDT, HEINZ

Inventor name: MUTHMANN, ERHARD, DR.

Inventor name: HECK, GUENTER

Inventor name: ROSSMEISSL, RUDOLF