EP0017202B1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0017202B1
EP0017202B1 EP80101693A EP80101693A EP0017202B1 EP 0017202 B1 EP0017202 B1 EP 0017202B1 EP 80101693 A EP80101693 A EP 80101693A EP 80101693 A EP80101693 A EP 80101693A EP 0017202 B1 EP0017202 B1 EP 0017202B1
Authority
EP
European Patent Office
Prior art keywords
tube
heat exchanger
width
diameter
height
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
EP80101693A
Other languages
German (de)
English (en)
Other versions
EP0017202A3 (en
EP0017202A2 (fr
Inventor
Fritz O. Schwenkler
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE19792912998 external-priority patent/DE2912998A1/de
Priority claimed from DE19803005958 external-priority patent/DE3005958A1/de
Application filed by Individual filed Critical Individual
Priority to AT80101693T priority Critical patent/ATE933T1/de
Publication of EP0017202A2 publication Critical patent/EP0017202A2/fr
Publication of EP0017202A3 publication Critical patent/EP0017202A3/de
Application granted granted Critical
Publication of EP0017202B1 publication Critical patent/EP0017202B1/fr
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
    • F28D7/10—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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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

Definitions

  • the invention relates to an arrangement for heat exchange with at least one tube provided with a number of annular ribs, with a closely surrounding the ribs-sending guide body and an inflow nozzle and an outflow channel, wherein the height of the ribs of the finned tube is smaller than the diameter of the pipe.
  • Such an arrangement is known from DE-A-19 40 963.
  • the width E of the inflow opening of the inflow nozzle is smaller than the diameter of the tube and that the width A of the outflow opening of the outflow channel is smaller than the inlet opening of the inflow nozzle.
  • the width of the inflow nozzle first decreases in the direction of the flow direction to a smallest value E and then increases again by a small amount.
  • the proposed arrangement considerably improves the heat transfer values between the heat-carrying medium and the finned tubes.
  • Another advantage of the proposed arrangement is the lower tendency towards contamination, because the heat exchange tube is completely flowed around, so that, as in known arrangements, partial areas of the exchange surface do not lie in the “dead water of the flow”.
  • the width of the inflow opening is approximately the difference between the diameter of the tube and the simple height of a rib and / or that the width of the outlet opening A corresponds to approximately twice the height of a rib.
  • the height r of the ribs of the tube is approximately 0.15 to 0.3 times the diameter of the tube. With these values, the rib efficiency is particularly favorable. Furthermore, it is advantageous according to the invention that the diameter of the tube is at least 70 mm and the minimum thickness of a rib is 1.5 mm. With this increase in the pipe diameter, the heat transfer improves.
  • the guide bodies consist of two sheet metal bodies which are bent in a semicircular shape and are fastened in a housing.
  • the guide bodies consist of sheet metal parts bent in a quarter circle, the inflow openings lying opposite each other and being spatially offset from one another by approximately 90 ° with respect to the outflow channels.
  • the outflow opening of the outflow channel is formed from sheet metal parts running in parallel.
  • a further tube is provided which is arranged concentrically to the finned tube and which is connected via a flange to a further flange arranged on the finned tube.
  • This arrangement allows the inner tube to be easily removed, which allows convenient control of the inner exchange surface in heat exchangers which are subject to a safety check.
  • the outer tube is conveniently closed at its end with a bottom.
  • the ribbing and the outer tube only extend over part of its length.
  • the cross-section of the non-finned part of the tube is expanded and a flange that can be connected to a housing and a pipe socket are arranged on this part.
  • 5 is the finned tube, on which annular fins 3 are arranged, designated. It is composed of two semicircular vanes.
  • Fig. 1 are designed as flow baffles 4, surrounded so that an annular gap 2 is formed between the baffles 4 and the tube 5.
  • Both flow guide plates 4 go in the axial direction into an inflow nozzle 1, which runs parallel to the finned tube 5 and has an inflow opening. 1.1 and an outflow channel 1.2.
  • the inflow nozzles 1 and the outflow channels each consist of sheets which are fastened to a housing 21.
  • the width E of the inflow nozzle 1 first decreases in the direction of the flow direction to a minimum value E and then increases again by a small amount,
  • the smallest width of the inlet opening 1.1 of the nozzle is smaller than the diameter of the tube 5. Very favorable heat transfer values can be achieved if the width of the inlet opening corresponds approximately to the difference between the sizes of the tube diameter d and the simple height r of a rib 3.
  • the width A of the outflow opening of the outflow channel 1.2 is smaller than that of the inlet opening 1.1. Very favorable heat transfer values can be achieved with a width A of the outlet opening if this corresponds approximately to twice the height r of a rib 3.
  • the flow guide plates are each designed in a quarter circle and the two inflow openings lie opposite one another, while the two outflow openings are each offset by 90 ° with respect to the outflow openings.
  • a second tube 6 is arranged concentrically to the finned tube and fixed in position by spacers 7.
  • One end of the finned tube 5 is closed by a base 8.
  • the ribbing of the outer tube 5 extends only over part of its length. It increases in diameter outside the ribbing and ends in a flange 15 which is connected to a flange 14 of the inner tube 6.
  • a pipe socket 10 is arranged on the non-finned part of the tube 5, through which one of the two gases or liquids can flow.
  • the finned tube 5 is provided in its wider section 3.1 with a further flange 16 which is connected to the flange 13 of a housing 21.
  • a further flange 16 which is connected to the flange 13 of a housing 21.
  • the gas or liquid flows into the housing from the left in the direction of the arrow in FIG. 1 and is passed through the inflow nozzle 1 into the annular gap 2 between the finned tube 5 of the flow guide plates 4.
  • the gas or liquid enters from two opposite points and flows around the finned tube only by 90 ° in each case in order to emerge again at the two outlet openings.
  • This arrangement is particularly advantageous in the case of pulsating flows, since vibrations are prevented by the flow from two sides.
  • the heat exchange tube can be conveniently pulled out of the housing 12 after loosening the housing flange connection 13.
  • the expansion of the inner tube 6 is possible by loosening the flange connection 14, so that simple assembly and inexpensive maintenance and cleaning of the heat exchanger is possible.

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)

Claims (10)

1. Agencement pour l'échange de chaleur avec au moins un tube (5) pourvu d'un certain nombre d'ailettes semi-circulaires (3), avec un corps directeur (4) entourant étroitement les ailettes (3) et avec une tuyère d'entrée d'écoulement (1.2), la hauteur (r) des ailettes (3) du tube aileté (5) étant plus petite que le diamètre (d) du tube (5), caractérisé en ce que la plus petite largeur (E) de l'orifice d'entrée d'écoulement (1.1) est plus petite que le diamètre (d) du tube (5) et en ce que la largeur (A) de l'orifice de sortie d'écoulement du conduit de sortie d'écoulement (1.2) est plus petite que celle (E) de l'orifice d'entrée (1.1) de la tuyère d'entrée d'écoulement (1).
2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que la largeur (E) de. l'orifice d'entrée d'écoulement (1.1) correspond au plus à la différence entre le diamètre (d) du tube (5) et la . hauteur simple (r) d'une ailette (3).
3. Echangeur de chaleur selon la revendication 2, caractérisé en ce que la largeur (A) de l'orifice de sortie d'écoulement du conduit de sortie d'écoulement (1.2) correspond à environ deux fois la hauteur (r) d'une ailette (3).
4. Echangeur de chaleur selon l'une des revendications 1 à 3, caractérisé en ce que la hauteur (r) des ailettes (3) du tube (5) est égale à environ 0,15 à 0,3 fois le diamètre du tube (5).
5. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que le diamètre du tube (5) est d'au moins 70 mm et l'épaisseur minimale d'une ailette (3) est de 1,5 mm.
6. Echangeur de chaleur selon l'une des reve- dications précédentes, caractérisé en ce que les corps directeurs (4) se composent de deux corps en tôle courbés semi-circulairement et fixés dans une enveloppe (figure 1).
7. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que les corps directeurs se composent d'éléments de tôle (4.1) courbés en forme de quart de cercle, auquel cas les orifices d'entrée d'écoulement (1.1) sont respectivement opposés mutuellement et sont disposés en étant respectivement décalés d'environ 90° dans l'espace par rapport aux conduits de sortie d'écoulement (1.2) (figure 2).
8. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que l'orifice de sortie d'écoulement du conduit de sortie d'écoulement (1.2) est formé par des éléments de tôle s'étendant parallèlement.
9. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce qu'à l'intérieur du tube à ailettes (5) est disposé, concentriquement à celui-ci, un autre tube (6) qui est relié par l'intermédiaire d'une bride (14) à une autre bride (15) disposée sur le tube à ailettes (5) et en ce que le tube à ailettes extérieur (5) est fermé à son extrémité par un fond (8).
10. Echangeur de chaleur selon l'une des revendications précédentes, caractérisé en ce que l'ailetage du tube à ailettes extérieur (5) s'étend seulement sur une partie de sa longueur et en ce que, sur la partie non ailetée du tube (5), sa section transversale s'élargit et sur cette partie sont disposées une bride (16) pouvant être raccordée à une enveloppe (21) ainsi qu'une tubulure de raccordement (10).
EP80101693A 1979-03-31 1980-03-29 Echangeur de chaleur Expired EP0017202B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80101693T ATE933T1 (de) 1979-03-31 1980-03-29 Waermeaustauscher.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19792912998 DE2912998A1 (de) 1979-03-31 1979-03-31 Waermeaustauschrohr mit aeusseren stroemungsleitblechen
DE2912998 1979-03-31
DE3005958 1980-02-16
DE19803005958 DE3005958A1 (de) 1980-02-16 1980-02-16 Waermeaustauscher

Publications (3)

Publication Number Publication Date
EP0017202A2 EP0017202A2 (fr) 1980-10-15
EP0017202A3 EP0017202A3 (en) 1980-11-26
EP0017202B1 true EP0017202B1 (fr) 1982-04-28

Family

ID=25778514

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80101693A Expired EP0017202B1 (fr) 1979-03-31 1980-03-29 Echangeur de chaleur

Country Status (2)

Country Link
EP (1) EP0017202B1 (fr)
DE (1) DE3060325D1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU1252892A (en) * 1991-02-08 1992-09-07 Anthony Hamilton Ive Heat-transfer conduits for use particularly in solar heating systems, and improvements relating to such systems
CN110030849A (zh) * 2019-04-17 2019-07-19 苏宇贵 壳管换热装置及其使用方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE138943C (fr) *
DE335361C (de) * 1921-03-31 Dipl Jng Heinrich Foege Waermeaustauschvorrichtung fuer Roehrensysteme
GB500389A (en) * 1937-11-16 1939-02-08 British Leyland Motor Corp Improvements in and relating to tubular heat exchangers for fluids
FR841618A (fr) * 1938-01-28 1939-05-24 Procédé d'échange de calories, et dispositifs de construction
GB850532A (en) * 1957-09-20 1960-10-05 Carves Simon Ltd Improvements in and relating to heat exchangers
GB934631A (en) * 1959-12-11 1963-08-21 Andre Huet Tubular heat exchanger
US3160145A (en) * 1962-07-20 1964-12-08 Avy L Miller Fluid heater
DE1940963A1 (de) * 1969-08-12 1971-02-25 Maschf Augsburg Nuernberg Ag Waermetauscher aus quer angestroemten Rippenrohren

Also Published As

Publication number Publication date
EP0017202A3 (en) 1980-11-26
EP0017202A2 (fr) 1980-10-15
DE3060325D1 (en) 1982-06-09

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