EP0074384B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP0074384B1
EP0074384B1 EP19820901030 EP82901030A EP0074384B1 EP 0074384 B1 EP0074384 B1 EP 0074384B1 EP 19820901030 EP19820901030 EP 19820901030 EP 82901030 A EP82901030 A EP 82901030A EP 0074384 B1 EP0074384 B1 EP 0074384B1
Authority
EP
European Patent Office
Prior art keywords
shell
finned tube
heat exchanger
tube
chamber
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
EP19820901030
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0074384A1 (en
Inventor
Gert Ake Elof Akerman
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.)
Uponor Wirsbo AB
Original Assignee
Wirsbo Bruks AB
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 Wirsbo Bruks AB filed Critical Wirsbo Bruks AB
Priority to AT82901030T priority Critical patent/ATE11821T1/de
Publication of EP0074384A1 publication Critical patent/EP0074384A1/en
Application granted granted Critical
Publication of EP0074384B1 publication Critical patent/EP0074384B1/en
Expired 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
    • F28D7/02—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
    • F28D7/10—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

Definitions

  • the present invention is related to a heat exchanger providing heat transfer between two mediums.
  • the heat exchanger comprises a tubular shell and a finned tube provided in the shell, the fins of the tube being substantially perpendicular to the direction of the tube.
  • One medium is flowing in the shell outside the finned tube and the other medium is flowing in the finned tube.
  • the heat exchanger is particularly intended for use in vapour condensers, e.g. in connection with heat pumps and similar devices in which the vapour is routed through the shell outside the finned tube and a cooling medium is routed through the finned tube.
  • a heat exchanger which comprises a tubular shell and a finned tube provided within the shell.
  • the fins on the tube are substantially perpendicular to the direction of the tube.
  • the internal cross-sectional area of the shell is longer than the area enclosed by the outer periphery of the fins. Vapour to be condensed is passed through the shell outside the finned tube and a coolant to condense the vapour is passed through the finned tube.
  • the shell is divided by the finned tube into chambers which are provided on respective sides of the finned tube.
  • the finned tubes are advantageous due to their large heat transfer surfaces. While these prior art heat exchangers can be used for condensing vapour, they have in this use the disadvantage that the condensate has a tendency to remain on the fin surfaces, thus reducing the capacity of the heat exchanger and slowing down the condensation process.
  • the main object of the invention is to provide a heat exchanger utilising the advantage of the large heat transfer surfaces of finned tubes but eliminating or at least reducing the tendency of the condensate to remain on the heat transfer surfaces.
  • the present invention provides a heat exchanger for condensing a vapour, comprising a tubular shell and a finned tube provided in the shell, the fins of the tube being substantially perpendicular to the direction of the tube, the internal cross sectional area of the shell being larger than the area enclosed by the outer periphery of the fins, the arrangement being such that vapour to be condensed may pass through the shell outside the finned tube and a coolant to condense said vapour may pass through the finned tube, wherein the shell is divided by the finned tube into chambers which are provided on respective sides of the finned tube and wherein only two chambers are formed within the shell, the first chamber being provided above the second chamber the first chamber having an inlet through which said vapour may be introduced to the heat exchanger and the second chamber having an outlet through which condensate may be removed from the heat exchanger.
  • the vapour can flow between the fins of the finned tube in good contact with the fins, thus providing a good heat transfer between the vapour flowing in the shell outside the finned tube and the coolant flowing in the finned tube. If the tube fins abut two opposite walls of the shell, a good heat transfer may also be provided between the finned tube and the shell, so that the shell will form a heat transfer surface for further improving the heat exchange between the two mediums passing through the heat exchanger.
  • the finned tube By positioning the finned tube diagonally in the shell, so that at the inlet end of the shell the first chamber occupies the larger portion of the space available outside the finned tube and at the outlet end of the shell the other chamber occupies the larger portion of the space available outside the finned tube, a comparatively large inlet and outlet can be provided, although the shell has a relatively small cross sectional area.
  • comparatively large amounts of the said vapour can be fed into the shell, enabling the transfer of relatively large amounts of heat between the vapour and the coolant.
  • the vapour flowing between the fins will tend to remove the condensate from the fin surfaces, so that the condensate does not remain on the fins and prevent further condensation.
  • This effect has been found to be particularly evident when the first chamber, i.e. the inlet chamber, in the shell is positioned above the second chamber, i.e. the outlet chamber.
  • the shell By designing the shell as an upright coil having a steep pitch, the condensate can be collected in the lower portion of the coil, where it will surround the finned tube, thus supercooling the condensate.
  • the embodiment of the invention shown in Figure 1 comprises a tubular outer shell 10 having substantially oval cross section, as shown in Figure 2.
  • a finned tube 11 is inserted in the shell 10.
  • the fins 12 of the tube consist of annular discs provided substantially perpendicularly to the longitudinal direction of the tube.
  • the fins of tubes of this type are normally made by rolling and turning tubes having thick walls, so that the fins form an integral part of the tube. Alternatively, the fins can form a helix surrounding the tube along its length.
  • the fins 12 of the finned tube 11 abut two opposed walls of the shell 10, as is shown in Figure 2.
  • the shell having a larger cross sectional area than the finned tube, is divided into two chambers 13, 14 by the finned tube 11, the chambers running from one end of the shell to the other and being provided on respective sides of the finned tube, so that the medium entering the first chamber 13 has to flow between the fins 12 of the tube to enter the second chamber 14.
  • the shell 10 is a straight tube into which a straight finned tube 11 has been inserted diagonally, so that at the inlet end of the shell the first chamber 13 occupies the larger portion of the space available outside the finned tube, and at the outlet end the second chamber 14 occupies the larger portion of the space available outside the finned tube.
  • This facilitates the attachment of inlet and outlet pipes 15, 16 and the pipes 15, 16 can be comparatively thick, even though the shell has a small cross-section.
  • the finned tube 11 is also provided with an inlet pipe 17 and an outlet pipe 18 for the medium flowing through the finned tube, the inlet and outlet pipes of the finned tube, however, being reversed as compared with the corresponding pipes of the shell, so that the two mediums will flow in opposite directions through the heat exchanger.
  • the flow directions of the mediums are indicated by arrows in Figure 1.
  • the heat exchanger according to the invention is intended to be used for condensing vapour.
  • the shell of the heat exchanger is preferably designed as an upright helical coil having a steep pitch.
  • An embodiment of this type is shown in Figure 3, where the same reference numerals as in Figure 1 have been used for the corresponding elements.
  • the finned tube 11 has been positioned diagonally in the shell 10 in this embodiment, as in the first, so that the inlet pipe 17 of the finned tube at the outlet end of the shell is situated in the upper portion of the shell and the outlet pipe 18 of the tube at the inlet end of the shell is situated in the lower portion of the shell.
  • the first chamber 13 of the shell is positioned above the second chamber 14.
  • the shell could have a circular cross section, but in that case sealing elements have to be provided between the finned tube and the walls of the shell, so that two separate chambers are formed in the shell, the chambers being connected to each other only through the spaces between the fins of the tube.
  • sealing elements may be used also when the shell has an oval or elongate cross section.
  • the finned tube need not necessarily run diagonally through the shell but can alternatively run along the central axis of the shell.
  • the shell must be sealed at its end by special walls.
  • the closure of the shell at the ends may be provided by deformation of the shell to contact the inlet and outlet pipes, the complete sealing then being provided by, for example, soldering.
  • the major axis of the cross section bf the shell is preferably parallel to the axis of the coil, as this will make it easier to wind the coil with a small diameter.
  • the lower wall of the shell has a shape that at least slightly differs from the shape of the fins, so that the condensate can flow in the shell along the full length of the shell.

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)
EP19820901030 1981-03-20 1982-03-19 Heat exchanger Expired EP0074384B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82901030T ATE11821T1 (de) 1981-03-20 1982-03-19 Waermeaustauscher.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8101808 1981-03-20
SE8101808A SE445138B (sv) 1981-03-20 1981-03-20 Anordning for vermevexling mellan tva medier for kondensering av anga

Publications (2)

Publication Number Publication Date
EP0074384A1 EP0074384A1 (en) 1983-03-23
EP0074384B1 true EP0074384B1 (en) 1985-02-13

Family

ID=20343392

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820901030 Expired EP0074384B1 (en) 1981-03-20 1982-03-19 Heat exchanger

Country Status (7)

Country Link
EP (1) EP0074384B1 (da)
JP (1) JPS58500378A (da)
DE (1) DE3262274D1 (da)
DK (1) DK151357C (da)
FI (1) FI74806C (da)
SE (1) SE445138B (da)
WO (1) WO1982003270A1 (da)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3300929A1 (de) * 1983-01-13 1984-07-19 Ulf Dipl.-Ing. Dr. 3404 Adelebsen Bossel Waermetauscher fuer ein kondensierendes oder verdampfendes medium und ein medium ohne phasenuebergang
US4562697A (en) * 1984-12-10 1986-01-07 Merlin Marine Engine Corp. Intercooler for turbocharged internal combustion engine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1927079A (en) * 1932-03-25 1933-09-19 Nat Radiator Corp Heat convector
US1953324A (en) * 1933-04-17 1934-04-03 Nat Radiator Corp Convector
US3443633A (en) * 1967-03-30 1969-05-13 Gen Electric Temperature compensated air-cooled steam condenser
DE2013940A1 (de) * 1970-03-24 1971-10-07 Schmoele Metall R & G Wärmeübertrager für flüssige und gasförmige Medien
SE374429B (da) * 1972-09-13 1975-03-03 Saab Scania Ab
CH635517A5 (de) * 1979-01-12 1983-04-15 Heatrans Ag Kaeltetrockner-vorrichtung fuer komprimierte luft.
EP0044349A1 (de) * 1980-07-18 1982-01-27 Riedel Kälte- und Klimatechnik GmbH & Co, KG Kondensator, insbesondere für Kälteanlagen und/oder Wärmepumpen

Also Published As

Publication number Publication date
SE8101808L (sv) 1982-09-21
JPS58500378A (ja) 1983-03-10
FI74806B (fi) 1987-11-30
DK151357C (da) 1988-07-04
WO1982003270A1 (en) 1982-09-30
FI74806C (fi) 1988-03-10
EP0074384A1 (en) 1983-03-23
DK151357B (da) 1987-11-23
FI823977L (fi) 1982-11-19
DE3262274D1 (en) 1985-03-28
DK516682A (da) 1982-11-19
FI823977A0 (fi) 1982-11-19
SE445138B (sv) 1986-06-02

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