EP0097726B1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP0097726B1
EP0097726B1 EP19820105574 EP82105574A EP0097726B1 EP 0097726 B1 EP0097726 B1 EP 0097726B1 EP 19820105574 EP19820105574 EP 19820105574 EP 82105574 A EP82105574 A EP 82105574A EP 0097726 B1 EP0097726 B1 EP 0097726B1
Authority
EP
European Patent Office
Prior art keywords
manifold
plate
heat exchanger
fin
open
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
EP19820105574
Other languages
English (en)
French (fr)
Other versions
EP0097726A1 (de
Inventor
Irwin E. Rosman
William Richard Wagner
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.)
Boeing North American Inc
Original Assignee
Rockwell International Corp
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 Rockwell International Corp filed Critical Rockwell International Corp
Priority to DE8282105574T priority Critical patent/DE3279938D1/de
Priority to EP19820105574 priority patent/EP0097726B1/de
Publication of EP0097726A1 publication Critical patent/EP0097726A1/de
Application granted granted Critical
Publication of EP0097726B1 publication Critical patent/EP0097726B1/de
Expired legal-status Critical Current

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    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F28D9/0018—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form without any annular circulation of the heat exchange media
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media

Definitions

  • the present invention relates to a heat exchanger in accordance with the prior art portion of claim 1.
  • a heat exchanger having the features indicated in the prior art portion of claim 1 is known by EP-A-44 561 (Fig. 10).
  • This prior art heat exchanger requires complicated additional separate inlet and outlet means.
  • the panel design comprises two different types of panels arranged alternatingly requiring the complicated inlet and outlet structure.
  • the plate/fin type heat exchangers are mainly of the channel and rib type construction. Countercurrent flow can be achieved. however. manifolding a plate stack which must separate the fluids at entry and exit becomes extremely complex. In that manifolding of the crosscurrent heat exchangers is comparatively simple, this heat exchanger system is more widely used although it is less efficient than the countercurrent system and it induces serious thermal and mechanical stresses.
  • Campbell et al One countercurrent system which has attempted to solve the manifolding problem of the countercurrent heat exchanger is taught by Campbell et al. U.S. Patent 3.305,010.
  • Campbell et al teach a heat exchanger having superposed stacked plate and fin elements and complex manifolding means for introducing fluids of different temperatures into opposite ends of the assembly.
  • Campbell et al do not teach a plate which serves as both the plate and the fin, nor does Campbell et al teach means for internally manifolding the plate within the plate's plane.
  • FIG. 1 Another countercurrent system, Fig. 1, is that of Alfa-Laval described in the Proceedings of the 5th OTEC Conference, Miami, Florida (Feb. 1978) Pages VI 288-320.
  • the Alfa-Laval concept consists mainly of a pack of thin metal plates, a frame and means of keeping the pieces together.
  • the plates are suspended between horizontal carrying bars at top and bottom and compressed against the stationary frame plate by means of tightening bolts and a movable pressure plate.
  • the frame plate is equipped with nozzles for inlet and outlet connections. Every plate is sealed around its perimeter with a gasket and cemented into a pressed track. Flow ports at each of the plate corners are individually gasketed and thus divide the interplate spaces into two systems of alternating flow channels.
  • the plate which is the basic element of this concept, has a corrugated pattern stamped on it. These corrugations can be arranged to create an unlimited number of plate patterns. The specific pattern results from a careful trade-off between drop and convective heat transfer characteristics.
  • the gaskets in the Alfa-Laval system are cemented to the plates in pressed tracks, and are generally made of elastomers like natural rubber, nitrile, butyl, neoprene, viton, etc.
  • the material selection depends upon the working conditions, however, the upper limits are about 360 PSI and about 400°F.
  • the present invention is based on the object of providing a heat exchanger of the above-mentioned type having a simple unitary design not requiring complicated inlet and outlet means.
  • an internally manifolded fin plate for a plate/fin-type heat exchanger for a plate/fin-type heat exchanger.
  • plate 10 be of unibody construction, a plurality of components may be connected to make up a single plate.
  • Figs, 2a, 2b and 2c there is shown the basic unibody, one piece, fin plate 10 which comprises open-face 12, and side ports 14,14 transversely oriented through top edge 17 of fin plate 10.
  • a schematic representation of an internally manifolded plate stack 30 comprising a plurality of internally manifolded fin plates 10.
  • fin plates are stacked in a manner in alternating sequence. It should be noted, for each embodiment, that although the fins 22 are shown in a vertical line. they may be staggered, Fig. 7b. Also, although in the preferred operating conditions these fin plates are the same, the internal design on alternating fin plates may be varied to accomplish the desired thermodynamic effects.
  • a first fluid is conveyed in through side ports 14 of alternating fin plates, into internal manifold 16, along channels 20 formed by fins 22, and exits through end ports 24.
  • a second fluid of either higher or lower temperature is similarly introduced through the side ports 14 of the next alternating fin plate resulting in countercurrent flow.
  • this is the preferred direction of flow, it is within the scope of this invention to have flow in a reverse manner wherein the fluid enters through end ports 24, flows down the channel 20 into the internal manifold 16, and exits through side port 14.
  • the flow could also be parallel by introducing one fluid through the side port 14 and the other fluid through the end port 24 of the adjacent fin plate.
  • the first and second fluids may be the same or different and that depending upon thermodynamic requirements, more than two fluids may be used.
  • FIGs. 3a and 3b there is shown two additional embodiments of the internal manifolding means 16.
  • Said manifolding means 16 may have a tapered geometery as defined by an angle 33.
  • the internal manifold 16 has two side ports 14, 14 and the taper narrows as the fluid reaches mid-point 32. At mid-point 32 an optional barrier 34 can be inserted.
  • the embodiment shows internal manifold 16 having one side port 14 and the taper goes across the full width of the fin plate narrowing as it reaches the closed side 23.
  • FIG. 4a the fins 22 and channels 20 are randomly inserted within the main channel 20 of the basic fin plate 10.
  • fin geometry in Figs. 4b and 4c shows inline intermittent fin geometries. Intermittent fin row can either be alternating as shown in Fig. 4b, or inline as shown in Fig. 4c.
  • the channel surface may be either smooth or rough depending upon the specific design requirements, and it should be noted that no matter what fin geometry is used, the fins and channels are designed to enhance structural integrity as well as overall heat transfer performance. Also, channels may taper in both depth and width.
  • a plurality of channel and fin shapes there is shown a plurality of channel and fin shapes.
  • the most conventional channel and fin shape is that which is represented by channel 20 and fin 22.
  • channels of different configurations such as those with rounded corners 36, U-shaped 38, V-shaped 40, and trapezoidal-shaped 42, along with their respective fin shapes are also within the scope of the invention.
  • One critical feature of the present invention is that the channel and fins combine to enhance heat transfer and structural integrity while the channel itself is open-faced, thus allowing ease of manufacture.
  • the channels themselves may be either smooth or rough, or corrugated or have any other surface goemetry which would enhance flow and heat transfer.
  • Fin plate 62 is basically the same as fin plate 10, however, fin plate 62 additionally comprises closed end external manifold 64, open end external manifold 66, and two pairs of side manifolds 68, 70. Each pair of side manifolds comprise a side inlet manifold 68 and a diagonally located side closed manifold 70. All external manifolds are integral and contiguous with fin plate 10. Although external manifolds are shown with rectangular goemetries, any geometry capable of transferring fluid to and from the fin plate will work.
  • FIG. 6b there is shown the top view of the internally and interiorly manifolded open-faced fin plate 63.
  • Plate 63 is basically the same as fin 62, however, fin plate 63 additionally comprises closed end auxiliary manifold 64, open end auxiliarly manifold 66, two pairs of interior side manifolds 68, 70 and a pair of interior inlets 65.
  • Each pair of interior side manifolds comprise a side inlet manifold 68 and a diagonally located side closed manifold 70.
  • FIGs. 7a, 7b and 7c there is shown various views of an internally manifolded fin plate and plate stack assembly 72.
  • fin plates are stacked in an opposed manner in alternating sequence.
  • a first fluid is conveyed to inlet side manifold 68 wherein said fluid flows in through side port 14 along the internal manifolding means 16 and is turned to flow down channels 20 formed by fins 22.
  • This first fluid then flows out end port 24 and into open end auxiliary manifold 66.
  • From the auxiliary manifold 66 the first fluid is then conveyed to any appropriate location.
  • a second fluid either warmer or cooler than the first fluid is conveyed into the adjacent fin plates through its respective side inlet manifold 68.
  • the second fluid is conveyed in through entry port 14 along the internal manifold 16, down channels 20 and along fins 22. From there the second fluid exits into its respective open end secondary manifold 66 where it would be conveyed to any appropriate location.
  • Closed end secondary manifolds 64 and side closed manifolds 70 are used to make continuous secondary manifolds between alternating fin plates. It should be noted that although the side and end manifolds are shown to be rectangular in shape, any functional shape will have the desired effect.
  • heat exchanger fluids may be liquids or gases or combinations of liquids and gases.
  • various plate thicknesses, channel and fin ratios, length and width ratios and various thermally conductive materials can be used.
  • the following materials are. delineated by way of example; metals, ceramics polymers.
  • the above design is the first real automated means for manufacturing heat exchangers. This will reduce the labor manhours involved in cutting, brazing, welding, leak checking, etc., compared to tube in shell and plate/fin heat exchangers. Moreover, the scaling of the design allowed provides a wide latitude of sizes, materials and fluids.
  • each passage (cold or hot) has an adjacent passage (hot or cold) on each side.
  • Bonded joint 11 between plates 10 permits the thermal conduction from plate to plate and thereby considerably enhances heat exchanger efficiency over a non-contacting joint design such as the Alfda-Laval concept.
  • the tailoring of the coolant passages to provide variable flow area is allowed in the design, both in width and height with an appropriate change in wall and land thicknesses. In the basic heat exchange process, the best heat exchange efficiency is provided with a pure frictional flow process.
  • the internal manifolding feature allows for both a minimum flow entrance loss and the internal manifold design provides for heat exchange within the manifold section, thus providing for the highest efficiency in a given length design.

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  • 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 (5)

1. Ein Wärmetauscher mit einem Stapel von Rippenplatten (10), von denen jede mit einer Mehrzahl von einstückig vorstehenden Rippen (22) versehen ist, die eine Mehrzahl von Kanälen (20) und eine offene Endöffnung (24) zwischen denselben festlegen, mit einem lateral bezüglich der Rippen angeordneten geschlossenen Ende (18) und einem inneren Verzweigungsstück (16) zwischen den Rippen und dem geschlossenen Ende, wobei die Rippen und das geschlossene Ende dieselbe Höhe haben, wobei ferner der Wärmetauscher mit zwei Paaren von Seitenverzweigungsstücken (68,70) für die Strömung eines ersten und zweiten Fluids vorgesehen ist. dadurch gekennzeichnet, daß jede Rippenplatte benachbart zu dem geschlossenen Ende (18) und der offenen Endöffnung (24) ein äußeres Verzweigungsstück (64) mit geschlossenem Ende und ein äusseres Verzweigungsstück (66) mit offenem Ende aufweist, die jeweils einstückig und angrenzend bezüglich einer jeden Rippenplatte ausgebildet sind, wodurch die beiden Paare von Seitenverzweigungsstücken (68, 70) diagonal an jeder Seite einer jeden Platte angeordnet sind, wenn die Platten aufeinander in einer alternierenden Folge gestapelt sind.
2. Ein Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, daß die Enden der Kanäle (20), die von dem Endverzweigungsstück (16) entfernt sind, in Endöffnungen (24) der Endebene der Tafel (10) und der Platte (26) enden und Auslaßöffnungen bilden.
3. Ein Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Querschnitt des Endverzweigungsstückes (16) sich von der Öffnung in Richtung auf dessen Mittelabschnitt in Längsrichtung oder in Richtung auf das andere Ende (Fig. 3a, b) ändert.
4. Ein Wärmetauscher nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, daß das Verzweigungsstück lediglich eine Einlaßöffnung (Fig. 3b) aufweist.
5. Ein Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Tafel an dem Verzweigungsstückende ein geschlossenes äußeres Verzweigungsstück (64) sowie an dem Kanalöffnungsende einen offenen, äußeren Verzweigungsstückabschnitt (66) aufweist, der mit sämtlichen Endöffnungen (24) verbunden ist, daß offene, äußere Verzweigungsstückabschnitte (68) an der Außenseite der Tafelplattenseiten (62, 63) an den Enden des inneren Endverzweigungsstückes (16) und in Verbindung mit diesem vorgesehen sind, und daß geschlossene äußere Seitenverzweigungsstückabschnitte (70) an entsprechenden an den entgegengesetzten Enden der Seitenwände (62, 63) vorgesehen sind (Fig. 6).
EP19820105574 1982-06-24 1982-06-24 Wärmetauscher Expired EP0097726B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8282105574T DE3279938D1 (en) 1982-06-24 1982-06-24 A heat exchanger
EP19820105574 EP0097726B1 (de) 1982-06-24 1982-06-24 Wärmetauscher

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19820105574 EP0097726B1 (de) 1982-06-24 1982-06-24 Wärmetauscher

Publications (2)

Publication Number Publication Date
EP0097726A1 EP0097726A1 (de) 1984-01-11
EP0097726B1 true EP0097726B1 (de) 1989-09-13

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ID=8189100

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EP19820105574 Expired EP0097726B1 (de) 1982-06-24 1982-06-24 Wärmetauscher

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DE (1) DE3279938D1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2580794B1 (fr) * 1985-04-23 1989-05-19 Inst Francais Du Petrole Dispositif d'echange thermique utilisable notamment pour des echanges entre gaz
EP0206067A1 (de) * 1985-06-20 1986-12-30 Stettner & Co. Katalytisch wirksamer Baukörper aus Einzelelementen und Verfahren zum Herstellen dieser Baukörper
DE3522095A1 (de) * 1985-06-20 1987-01-02 Stettner & Co Vorrichtung zum behandeln stroemender medien und verfahren zu ihrer herstellung
DE19510847C2 (de) * 1995-03-17 2002-11-21 Michael Rehberg Plattenwärmetauscher
SE534381C2 (sv) * 2009-12-08 2011-08-02 Ny Kraft Sverige Ab Värmeväxlare med flödesstyrande limmönster samt metod att framställ denna
CN115183611B (zh) * 2022-09-08 2022-11-18 中国核动力研究设计院 换热部件

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE143252C (de) *
US1662870A (en) * 1924-10-09 1928-03-20 Stancliffe Engineering Corp Grooved-plate heat interchanger
GB327377A (en) * 1928-03-07 1930-04-03 Richard Seligman Improvements in or relating to plate heat exchange apparatus employing condensable gas or fluid
GB743201A (en) * 1953-01-28 1956-01-11 William Helmore Improvements in or relating to heat exchangers
GB1048122A (en) * 1966-08-12 1966-11-09 Nicholson Terence Peter Improvements in and relating to plate type heat exchangers
US3613782A (en) * 1969-08-27 1971-10-19 Garrett Corp Counterflow heat exchanger
US3818984A (en) * 1972-01-31 1974-06-25 Nippon Denso Co Heat exchanger
DE2706253A1 (de) * 1977-02-15 1978-08-17 Rosenthal Technik Ag Keramischer, rekuperativer gegenstromwaermetauscher
EP0044561A3 (de) * 1980-07-21 1982-07-14 MüANYAGIPARI KUTATO INTEZET Wärmetauscher, insbesondere zum Wärmeaustausch zwischen gasförmigen Medien

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Publication number Publication date
DE3279938D1 (en) 1989-10-19
EP0097726A1 (de) 1984-01-11

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