DK152625B - HEAT EXCHANGING - Google Patents
HEAT EXCHANGING Download PDFInfo
- Publication number
- DK152625B DK152625B DK131176AA DK131176A DK152625B DK 152625 B DK152625 B DK 152625B DK 131176A A DK131176A A DK 131176AA DK 131176 A DK131176 A DK 131176A DK 152625 B DK152625 B DK 152625B
- Authority
- DK
- Denmark
- Prior art keywords
- guide plate
- heat exchanger
- tubes
- exchanger according
- medium
- Prior art date
Links
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000004020 conductor Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000005028 tinplate Substances 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F28D7/04—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 spirally coiled
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
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)
Description
Opfindelsen angår en varmeveksler af den i krav l’s indledning angivne art.The invention relates to a heat exchanger of the kind specified in the preamble of claim 1.
Sådanne varmevekslere er mest effektive, når man indretter dem således, at begge medierne går i en ren modstrøm mod hinanden. Ved varmevekslere med små rør, hvor rørene af pladshensyn er opviklet i en spiral, er det kendt at frembringe en ren modstrøm ved, at man lader en tæt ledeblikplade følge med i spiralen og på denne måde tvinge mediet uden for spiralrøret til at følge røret i hele dettes længde.Such heat exchangers are most effective in aligning them so that both media run in a clean countercurrent to each other. In small-tube heat exchangers, where the tubes are coiled in a spiral for reasons of space, it is known to produce a pure countercurrent by allowing a dense lead sheet plate to follow in the spiral, thereby forcing the medium outside the spiral tube to follow the tube. its entire length.
Der findes mange anvendelsesområder for varmevekslere af den foreliggende art, f.eks. radiatorudvekslere, ventilationsudvekslere, vandvarmere for brugsvand til fjernvarme eller kølecentraler og udvekslere til markoverfladeopvarmning. Hvert anvendelsesområde har sit strømningsforhold mellem de to medier, afhængig af de ønskede temperaturforskelle og de tilgængelige trykfald. For en given rørdimension må strømningsarealet i kanalerne uden for rørene derfor varieres, hvis konstruktionen skal kunne tilpasses til de varierede krav.There are many applications for heat exchangers of the present type, e.g. radiator exchangers, ventilation exchangers, domestic water heaters for district heating or cooling plants and field surface heating exchangers. Each application has its flow ratio between the two media, depending on the desired temperature differences and the available pressure drops. Therefore, for a given pipe dimension, the flow area in the ducts outside the pipes must be varied if the structure is to be adapted to the varied requirements.
I tidligere kendte udførelser af sådanne varmevekslere har man anvendt det princip, at rørspiralerne placeres i en stabel med en for hvert anvendelsesområde hensigtsmæssig afstand mellem de forskellige lag i stablen. Alternativt kan spiralens stigning anvendes som en variabel til tilpasning af af konstruktionen til et vist anvendelsesområde. I begge tilfælde får man fremstillingsmæssige komplikationer, der bidrager til, at varmevekslerne bliver dyre. Desuden betyder det, at de fleste varmevekslere får unødig stor byggevolumen, hvad der medfører forøgede omkostninger og problemer med installationen.In prior art embodiments of such heat exchangers, the principle has been used that the pipe spirals are placed in a stack with a suitable distance for each application area between the different layers of the stack. Alternatively, the rise of the coil can be used as a variable for adapting the structure to a certain application. In both cases, there are manufacturing complications that contribute to the cost of heat exchangers. In addition, this means that most heat exchangers get an unnecessarily large building volume, which leads to increased costs and installation problems.
Den foreliggende opfindelse tager sigte på at angive en varmeveksler af den nævnte art, ved hvilken de omtalte ulemper er undgået, og dette opnås ifølge opfindelsen ved, at varmeveksleren er udformet som angivet i krav l's kendetegnende del.The present invention aims to provide a heat exchanger of the kind in which the said drawbacks are avoided and this is achieved according to the invention in that the heat exchanger is designed as defined in the characterizing part of claim 1.
Herved opnar man, at man i én og samme konstruktion, i stedet for at forøge strømningsarealet i kanalerne uden for rørene, når strømmen dér er større end normalt, kan bibeholde en vis deling mellem spiralerne og også kan bibeholde spiralernes stigning, men kan forkorte strømningsvejen ved, at strømmen lokalt til en vis grad "kortsluttes" ved overstrømning mellem to op til hinanden liggende vindinger i spiralen. Denne kortslutning kan ved praktisk fremstilling ske lokalt i et antal punkter, der eventuelt kan være meget stort. Effektiviteten af modstrømsvarmeveksleren påvirkes ikke nævneværdigt herved.This provides that in one and the same construction, instead of increasing the flow area in the ducts outside the pipes, when the flow there is greater than normal, a certain division between the coils can be maintained and also can maintain the rise of the coils, but can shorten the flow path in that the current is "short-circuited" locally to a certain extent by overflow between two adjacent turns of the coil. This short circuit can, by practical manufacture, take place locally in a number of points which may be very large. The efficiency of the countercurrent heat exchanger is not significantly affected.
Opfindelsen forklares nærmere under henvisning til tegningen, på hvilken· fig. 1 viser et lodret snit gennem en udførelsesform for varmeveksleren ifølge opfindelsen, og fig. 2 varmevekslerens indre del set fra oven og delvist i snit.The invention is explained in more detail with reference to the drawing, in which: FIG. 1 shows a vertical section through an embodiment of the heat exchanger according to the invention, and FIG. 2 The inner part of the heat exchanger as seen from above and partly in section.
Varmeveksleren har i den viste udførelse en beholder, der er sammensat af to gavlstykker 1 og 2 og en cylindrisk kappe 3. 1 det ene gavlstykke 2 udmunder et centralt rør 4, medens der igennem det andet gavlstykke 1 er ført to forgreningsrør 5 og 6. Endvidere udgår et rør 7 fra kappen. Mellem forgreningsrørene løber et antal rørspiraler 8, der ved den viste udførelse er ført tre og en halv vinding rundt om beholderens centrumsakse. Rørenes indre ender er forbundet med forgreningsrøret 5, medens de ydre ender er forbundet med forgreningsrøret 6. Rørspiralerne og forgreningsrørene danner en strømningsvej for det ene medium, medens beholderen iøvrigt og rørene 4 og 7 danner en strømningsvej for det andet medium.In the illustrated embodiment, the heat exchanger has a container composed of two end pieces 1 and 2 and a cylindrical sheath 3. In one end piece 2 opens a central pipe 4, while two manifolds 5 and 6 pass through the other end piece 1. Furthermore, a tube 7 exits the sheath. Between the manifolds, a plurality of tubing coils 8 run, which in the illustrated embodiment are guided three and a half turns around the center axis of the container. The inner ends of the tubes are connected to the manifold 5, while the outer ends are connected to the manifold 6. The pipe spirals and the manifolds form a flow path for one medium, while the container and tubes 4 and 7 form a flow path for the other medium.
I rørspiralerne er der indviklet en ledeblikplade 9, der strækker sig mellem gavlstykkerne 1 og 2 og danner et antal spiralformede kanaler 10 mellem rørene 8 og mellem disse og gavlstykkerne. Det andet medium tvinges gennem disse kanaler og bringes derved i nær kontakt med rørene. Som angivet i det foregående, bliver varmeveksleren mest effektiv, når de to medier strømmer i modstrøm mod hinanden. I det aktuelle tilfælde skal det ene medium derfor strømme med uret i fig. 2 og det andet mod uret f.eks. som vist ved retningen af pile 11 og 12 i fig· 2.In the pipe spirals, a guide plate 9 is wound which extends between the end pieces 1 and 2 and forms a plurality of helical channels 10 between the pipes 8 and between these and the end pieces. The second medium is forced through these channels and thereby brought into close contact with the tubes. As stated above, the heat exchanger becomes most effective when the two media flow counterclockwise. In the present case, therefore, one medium must flow clockwise in FIG. 2 and the other counterclockwise e.g. as shown by the direction of arrows 11 and 12 in Fig. 2.
For store gennemstrømningsmængder i kanalerne 10 har det vist sig, at trykfaldet gennem udveksleren bliver unormalt stort, hvorfor en afkortet strømningsvej for mediet ville være ønskelig. En sådan afkortet strømningsvej opnås ifølge opfindelsen ved, at man lader mange små strømvinkler successivt kortsluttes gennem overstrømning til den næste kanal 10 i spiralen.For excessive flow rates in the channels 10, it has been found that the pressure drop through the exchanger becomes abnormally large, which is why a shortened flow path for the medium would be desirable. Such a shortened flow path is obtained according to the invention by successively shorting many small angles of flow through overflow to the next channel 10 in the coil.
Konstruktivt kan denne overstrømning, som ved den viste udførelse, udføres ved hjælp af huller 13 i ledeblikpladen for hver kanal 10. Idet man varierer hullernes dimension og/eller huldelingen, kan udveksleren tilpasses til varierende krav om nedsættelse af strømningsmodstanden for det i kanalerne 10 strømmende medium, uden at man behøver at ændre spiralafstand eller stigning. Ændringen af huldelingen er en meget enkel foranstaltning ud fra et fremstillingssyns-punkt, hvorfor de store ulemper med de tidligere konstruktioner på denne måde kan undgås. Det er også muligt at gøre ledeblikpladerne udskiftelige og vælge en ledeblikplade for hver anvendelse med en huldeling og huldimensioner, der giver den bedste varmeudveksling ved en vis strømgennemgang. Valget af en sådan ledeblikplade medfører en forøget fleksibilitet i udvekslerens anvendelse, hvorfor de anvendte dele i udveksleren kan standardiseres, idet den eneste del, der skal udføres i et flertal modeller, bliver ledeblikpladen.Constructively, this overflow, as in the embodiment shown, can be effected by means of holes 13 in the guide plate for each channel 10. By varying the dimensions of the holes and / or the hole pitch, the exchanger can be adapted to varying requirements to reduce the flow resistance of the flowing in the channels 10. medium, without having to change the spiral distance or pitch. The alteration of the hole divide is a very simple measure from a manufacturing point of view, so the major disadvantages of the previous designs can be avoided in this way. It is also possible to make the conductor plates interchangeable and select a conductor plate for each application with a hole division and hole dimensions that provide the best heat exchange at a certain current flow. The choice of such a guide plate results in increased flexibility in the use of the exchanger, so the parts used in the exchanger can be standardized, with the only part to be performed in a plurality of models being the guide plate.
Den ovenfor beskrevne udførelse er et eksempel på, hvorledes opfindelsen kan realiseres. Ændringer i · denne udførelse kan foretages f.eks. ved at rørspiralerne, i stedet for cirkulært er opviklet i en vilkårlig oval form. Det-er også muligt at erstatte huldelingen i blikpladen med én eller flere afbrydelser i blikpladen, der så får form af et antal sektioner, idet afbrydelserne tjener som overstrømningssteder mellem to op til hinanden liggende kanaler 10, medens overstrømningsstedets "kapacitet" er bestemt af afbrydningens størrelse.The embodiment described above is an example of how the invention can be realized. Changes in · this embodiment can be made e.g. in that the tube spirals, instead of circular, are wound in any oval shape. It is also possible to replace the hollow partition of the tinplate with one or more interruptions in the tinplate, which then take the form of a number of sections, the interruptions serving as overflow sites between two adjacent channels 10, while the "capacity" of the overflow site is determined by the interruption size.
Claims (5)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE7504216 | 1975-04-14 | ||
SE7504216A SE400368B (en) | 1975-04-14 | 1975-04-14 | HEAT EXCHANGER |
Publications (3)
Publication Number | Publication Date |
---|---|
DK131176A DK131176A (en) | 1976-10-15 |
DK152625B true DK152625B (en) | 1988-03-28 |
DK152625C DK152625C (en) | 1988-08-22 |
Family
ID=20324263
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
DK131176A DK152625C (en) | 1975-04-14 | 1976-03-25 | HEAT EXCHANGING |
Country Status (7)
Country | Link |
---|---|
JP (1) | JPS603157B2 (en) |
CA (1) | CA1052765A (en) |
DE (1) | DE2615977A1 (en) |
DK (1) | DK152625C (en) |
FI (1) | FI63833C (en) |
FR (1) | FR2308071A1 (en) |
SE (1) | SE400368B (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4271900A (en) | 1978-06-28 | 1981-06-09 | E. I. Du Pont De Nemours And Company | Apparatus with expandable tube bundle |
FR2462684A1 (en) * | 1979-08-03 | 1981-02-13 | Saunier Duval | Spiral plate heat exchanger - contains parallel tubes joined by end headers with regular perforations |
DE3319385A1 (en) * | 1983-05-25 | 1984-11-29 | Donald Dipl.-Ing. 1000 Berlin Herbst | Heat exchanger |
DE3508240A1 (en) * | 1985-03-08 | 1986-09-11 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Heat exchanger, in particular charge air cooler with optimised flow resistances for all heat-exchanging media |
DE3925795A1 (en) * | 1989-08-04 | 1991-02-07 | Walter Englmann | Heat exchanger with spiral coils - which guided first medium while second medium flows through pipes forming spirals |
DE19510847C2 (en) * | 1995-03-17 | 2002-11-21 | Michael Rehberg | Plate heat exchanger |
AU778311B2 (en) * | 2002-04-11 | 2004-11-25 | Alan Paul Baker | Heat exchanger |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1092493B (en) * | 1958-04-24 | 1960-11-10 | Ver Economiser Werke G M B H | Tube bundle heat exchanger |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE273142C (en) * | 1912-10-15 | 1914-04-20 | ||
DE273765C (en) * | 1912-10-15 | 1914-05-06 | ||
US2856162A (en) * | 1956-01-17 | 1958-10-14 | Olin Mathieson | Heat exchanger |
US3006612A (en) * | 1958-03-17 | 1961-10-31 | Borg Warner | Heat exchangers |
US3173479A (en) * | 1959-09-30 | 1965-03-16 | Olin Mathieson | Heat exchanger |
US3120742A (en) * | 1960-10-24 | 1964-02-11 | Denisoff Alexander Constantine | Tank cooling system |
FR1403239A (en) * | 1964-07-02 | 1965-06-18 | Svenska Flaektfabriken Ab | heat exchanger |
CH456664A (en) * | 1965-12-20 | 1968-07-31 | Harzer Achsenwerke Kg Schweman | Spiral tube heat exchanger |
-
1975
- 1975-04-14 SE SE7504216A patent/SE400368B/en not_active IP Right Cessation
-
1976
- 1976-03-25 DK DK131176A patent/DK152625C/en not_active IP Right Cessation
- 1976-04-05 FI FI760906A patent/FI63833C/en not_active IP Right Cessation
- 1976-04-07 FR FR7610045A patent/FR2308071A1/en active Granted
- 1976-04-12 DE DE19762615977 patent/DE2615977A1/en active Granted
- 1976-04-12 CA CA250,023A patent/CA1052765A/en not_active Expired
- 1976-04-14 JP JP51041389A patent/JPS603157B2/en not_active Expired
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1092493B (en) * | 1958-04-24 | 1960-11-10 | Ver Economiser Werke G M B H | Tube bundle heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
DE2615977A1 (en) | 1976-10-28 |
CA1052765A (en) | 1979-04-17 |
JPS603157B2 (en) | 1985-01-25 |
DK131176A (en) | 1976-10-15 |
FR2308071B1 (en) | 1980-08-14 |
FI63833B (en) | 1983-04-29 |
DK152625C (en) | 1988-08-22 |
FR2308071A1 (en) | 1976-11-12 |
JPS51142151A (en) | 1976-12-07 |
DE2615977C2 (en) | 1988-09-15 |
SE400368B (en) | 1978-03-20 |
FI760906A (en) | 1976-10-15 |
SE7504216L (en) | 1976-10-15 |
FI63833C (en) | 1983-08-10 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUP | Patent expired |