EP0097726A1 - A heat exchanger - Google Patents
A heat exchanger Download PDFInfo
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- EP0097726A1 EP0097726A1 EP82105574A EP82105574A EP0097726A1 EP 0097726 A1 EP0097726 A1 EP 0097726A1 EP 82105574 A EP82105574 A EP 82105574A EP 82105574 A EP82105574 A EP 82105574A EP 0097726 A1 EP0097726 A1 EP 0097726A1
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- Prior art keywords
- plate
- manifold
- open
- integral
- contiguous
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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
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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
- 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
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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
- F28D9/0031—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
- This invention relates to plate/fin-type heat exchangers, and more specifically, to a unibody open-faced plate for plate/fin-type heat exchangers using countercurrent or parallel flow.
- 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.
- 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 can be distinguished from that of Alfa-Laval in many ways, some of which include: (1) that the Alfa-Laval system requires gaskets which limit operating pressure and temperature; (2) that the Alfa-Laval system has no contact fins or essential flat plate bottoms for providing the plate-to-plate contact necessary to obtain the optimum heat transfer coefficient; (3) the fact that the inlets and outlets of the Alfa-Lavel system are positioned on opposite ends but on the same side of the plate results in a mal- distribution of flow across the plate and inefficient heat transfer; and (4) that Alfa-Laval provides no means for driving the incoming fluid across the face of the plate, thereby correcting for their inherent inefficiencies.
- an open-faced internally manifolded unibody fin plate for use in a plate/fin-type heat exchanger.
- Each open-faced internally manifolded unibody fin plate comprises a side port contiguous with an internal manifolding means and wherein the manifolding means is transverse to a plurality of channels, and wherein each channel is contiguous with an end port.
- a plurality of the open-faced internally manifolded unibody fin plates can be stacked in an opposed manner in an alternating sequence. This internally manifolded plate stack can then be combined with external manifolds to yield an efficient low-cost countercurrent heat exchanger.
- Another variation of the open-faced unibody internally manifolded plate would include integral auxiliary inlet and outlet manifolds, thereby eliminating the need for separate external manifolding.
- Another object of the present invention is to provide a one-piece internall) manifolded fin plate for a plate/fin-type heat exchanger.
- 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 where in the fluid enters through end ports 24, flows down the channels 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.
- 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.
- the proposed plate stack design, Fig. 12c, heat exchanger provides for the optimum counterflow design together with extended surface finned construction and no corrugations (if minimum pressure loss is desired).
- a principal advantage is the intimate thermal joint provided by the plate stack which provides for thermal improvements for (almost) all circumstances.
- the plate-to-plate contact will mean the benefit of the superior thermal conduction of the metal not only between two adjacent plates but from other plates far removed from the immediate thermal joint.
- the added ability of the design to improve heat conduction results from the three-. dimensional thermal conduction within the plate stack.
- the better 3-D thermal conduction in the design also reduces the peak thermal stresses by the proportionate reduction in peak surface temperatures within the exchanger.
- Fig. 13 illustrates for the designs, the requirements of S' vs heat transfer coefficient. For all but the highest heat transfer rate conditions, a practical thickness can be found to use the IMPS plate stack approach.
- the overall heat transfer rate q/A for the plate stack heat exchanger on a unit surface area basis between plates may be expressed as (approximately): with more detailed analyses performed by computer solution.
- the cold side and hot side heat transfer coefficients (H h and H c ) become specified, and the wall heat flux can be optimized by the geometry and material selection.
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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)
Abstract
Description
- This invention relates to plate/fin-type heat exchangers, and more specifically, to a unibody open-faced plate for plate/fin-type heat exchangers using countercurrent or parallel flow.
- 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.
- 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. However, 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.
- 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. Through these, the two media pass, the warmer medium giving up heat to the cooler by conduction through the thin plates. This gasket arrangement eliminates the risk of media interleakage. 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 pressure 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 can be distinguished from that of Alfa-Laval in many ways, some of which include: (1) that the Alfa-Laval system requires gaskets which limit operating pressure and temperature; (2) that the Alfa-Laval system has no contact fins or essential flat plate bottoms for providing the plate-to-plate contact necessary to obtain the optimum heat transfer coefficient; (3) the fact that the inlets and outlets of the Alfa-Lavel system are positioned on opposite ends but on the same side of the plate results in a mal- distribution of flow across the plate and inefficient heat transfer; and (4) that Alfa-Laval provides no means for driving the incoming fluid across the face of the plate, thereby correcting for their inherent inefficiencies.
- Finally, it should be noted that the aforementioned prior art does not teach an annular plate structure nor the plate segment of the present invention.
- Accordingly, there is provided by the present invention an open-faced internally manifolded unibody fin plate for use in a plate/fin-type heat exchanger. Each open-faced internally manifolded unibody fin plate comprises a side port contiguous with an internal manifolding means and wherein the manifolding means is transverse to a plurality of channels, and wherein each channel is contiguous with an end port. A plurality of the open-faced internally manifolded unibody fin plates can be stacked in an opposed manner in an alternating sequence. This internally manifolded plate stack can then be combined with external manifolds to yield an efficient low-cost countercurrent heat exchanger. Another variation of the open-faced unibody internally manifolded plate would include integral auxiliary inlet and outlet manifolds, thereby eliminating the need for separate external manifolding.
- Therefore, it is an object of the present invention to provide an internally manifolded fin plate for use in a plate/fin-type heat exchanger.
- Another object of the present invention is to provide a one-piece internall) manifolded fin plate for a plate/fin-type heat exchanger.
- Yet another object of the present invention is to provide heat exchanger plates which can be made from a single die.
- Still another object of the present invention is to provide a highly efficient countercurrent or parallel flow plate/fin heat exchanger.
- Another object of the present invention is to provide high efficiency by having external or auxiliary manifolding which feeds fluid to an internal manifold especially designed to increase the length of fluid current path.
- Yet another object of the present invention is to provide low-cost assem by simple reversal of plates and bonding (diffusion bond, braze, weld) or bolt clamping a set of like plates.
- Another object of the present invention is to provide an open-faced fin plate which incorporates a plurality of fin configurations for enhancement of heat transfer through increased surface area and plate-to-plate contact.
- Still another object of the present invention is to provide a heat exchanger having simplified auxiliary manifolds.
- Yet a further object of the present invention is to provide a simple manifolding means for an internally manifolded plate stack.
- Still another object of the present invention is to provide a cost efficient and effective countercurrent or parallel flow heat exchanger.
- Another object of the present invention is to provide a heat exchanger having plates relatively free from mechanical and thermal stresses.
- Still another object of the present invention is to provide a heat exche which can be manufactured inexpensively.
- Other objects, advantages, and novel features of the present invention v become apparent from the following detailed description of the invention when considered in conjunction with the accompanying drawings, in which like reference numerals designate like parts throughout the figures.
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- Fig. 1 is prior art. It is a top view of the Alfa-Laval corrugated plate.
- Fig. 2a is a perspective schematic view of the open-faced internally manifolded fin plate.
- Fig. 2b is a top schematic view of the open-faced internally manifolded fin plate.
- Fig. 2c is an open-end schematic view of an open-faced internally manifolded plate.
- Fig. 2d is a perspective schematic view of an open-faced internally manifolded plate stack.
- Fig. 3a shows an additional schematic embodiment of the internal manifold for the open-faced internally manifolded plate.
- Fig. 3b shows another schematic embodiment of the internal manifold for the open-faced internally manifolded plate.
- Fig. 4a is the top view of another schematic embodiment of the fin-channel configuration.
- Fig. 4b is a top view of yet another schematic embodiment of the fin-channel configuration.
- Fig. 4c is a third schematic top view of a fin-channel configuration.
- Fig. 5 is a schematic end view of the open-faced internally manifolded fin plate showing various geometries of channels and fins.
- Fig. 6a is a schematic top view of an open-faced internally manifolded fin plate having integral external side and end manifolds.
- Fig. 6b is another schematic top view of an open-faced internally manifolded fin plate having integral interior side and end manifolds.
- Fig. 6c is a perspective view of another embodiment of an open-faced internally manifolded fin plate having integral interior corner manifolds.
- Fig. 6d is a top view of another embodiment of the flow guides for the fin plate depicted in Fig 6c.
- Fig. 7a is an enlarged fragmentary perspective showing relative proportions of fins and channels.
- Fig. 7b is a schematic view of the plate stack showing the fins in a vertically staggered relationship.
- Fig. 8a is a perspective view of a single internally and externally manifolded plate.
- Fig. 8b is a perspective view of the open-faced internally manifolded plate stack having side and end manifolds integrally connected with the open-faced internally manifolded plate.
- Fig. 8c is an enlarged fragmentary perspective showing relative proportions of fins, channels, and manifolding means.
- Fig. 9a is a schematic of the annular open-faced internally manifolded structure wherein each annular structure comprises a plurality of plates.
- Fig. 9b is a schematic cutaway view of the annular open-faced internally manifolded ring structure stack wherein each ring structure comprises a plurality of plates.
- Fig. 9c is an enlarged fragmentary perspective of Fig. 9a showing relative proportions of fins and channels.
- Fig. 10a is a schematic top view of an outlet plate for an annular open-faced internally manifolded plate.
- Fig. 10b is a schematic top view of an inlet plate for an annular open-faced internally manifolded plate.
- Fig. 11 is a graphical representation showing the effect of flow arrangement on exchanger performance.
- Fig. 12a is a schematic arrangement of a counterflow-waved wall heat exchanger.
- Fig. 12b is a schematic arrangement of a counterflow ribbed fin plate exchanger.
- Fig. 12c is a schematic arrangement of a counterflow plate stack heat exchanger.
- Fig. 13 is a graphical representation of advanced heat exchanger wall thickness limits.
- Fig. 14 is a graphical representation of the theoretical enhancement ratio vs fin height-to-width ratio.
- Fig. 15 is a graphical representation of the advanced Internally Manifolded Plate Stack (IMPS) overall film coefficient vs gas film coefficient.
- Fig. 16 is a graphical representation of performance degradation with Biot Number.
- In accordance with the present invention there is provided an internally manifolded fin plate for a plate/fin-type heat exchanger. Although it is preferred that
plate 10 be of unibody construction, a plurality of components may be connected to make up a single plate. Referring to Figs. 2a, 2b, and 2c, there is shown the basic unibody, one piece,fin plate 10 which comprises open-face-12, andside ports top edge 17 offin plate 10.Side ports Closed end 18 is adjacent to and lateral with the aft end of internal manifolding means 16.Channels 20 formed byfins 22 are contiguous with and transverse to the forward end of the manifolding means 16 and direct fluid flow to endports 24.Bottom 26 provides a heat transfer surface for connecting tofins 22 of an adjacent plate, a means for separating fluids, as well as a means for sealably connecting thefin plates 10 in a plate stack. It should be noted that the plate stack can be used for high or low pressure situations and that internal leakage paths are non-critical.Plate cover 15 can either be solid, as shown, or merely anotherbasic fin plate 10. Additionally, Fig. 2b showsoptional manifold fins 28.Manifold fins 28 provide added support and additional means to transfer heat. - Referring now to Fig. 2d, there is shown a schematic representation of an internally
manifolded plate stack 30 comprising a plurality of internallymanifolded fin plates 10. In the preferred operating condition, fin plates are stacked in an opposed manner in alternating sequence. It should be noted, for each embodiment, that although thefins 22 are shown in a vertical line, they s 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. In the preferred operating sequence, a first fluid is conveyed in throughside ports 14 of alternating fin plates, intointernal manifold 16, alongchannels 20 formed byfins 22, and exits throughend ports 24. A second fluid of either higher or lower temperature is similarly introduced through theside ports 14 of the next alternating fin plate resulting in countercurrent flow. Although this is the preferred direction of flow, it is within the scope of this invention to have flow in a reverse manner where in the fluid enters throughend ports 24, flows down thechannels 20 into'theinternal manifold 16, and exits throughside port 14. The flow could also be parallel by introducing one fluid through theside port 14 and the other fluid through theend port 24 of the adjacent fin plate. It should be noted that the first and second fluids may be the same or different and that depending upon thermodynamic requirements, more than two fluids may be used. - Referring now to Figs. 3a and 3b, there is shown two additional embodiments of the internal manifolding means 16. Said manifolding means 16 may have a tapered geometry as defined by an
angle 33. In Fig. 3a, the internal, manifold 16 has twoside ports optional barrier 34 can be inserted. In Fig. 3b, the embodiment showsinternal manifold 16 having oneside port 14 and the taper goes across the full width of the fin plate narrowing as it reaches theclosed side 23. Although there are only three internal manifolding geometries displayed herein, any other internal manifold geometry which could channel the fluid from aside port 14 to thechannels 20 is within the scope of this invention. - Referring now to Figs. 4a, 4b and 4c, there is shown additional geometries for
fins 22 andchannels 20. In Fig. 4a, thefins 22 andchannels 20 are randomly inserted within themain channel 20 of thebasic fin plate 10. In contrast to that, 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. - Referring now to Fig. 5, 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 andfin 22. However, channels of different configurations such as those withrounded 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. Additionally, it should be noted that the channels themselves may be either smooth or rough, or corrugated or have any other surface geometry which would enhance flow and heat transfer. - Referring now to Fig. 6a, there is shown the top view of the internally and auxiliary manifolded open-
faced fin plate 62.Fin plate 62 is basically the same asfin plate 10; however,fin plate 62 additionally comprises closed endexternal manifold 64, open endexternal manifold 66, and two pairs of side manifolds 68, 70. Each pair of side manifolds comprise aside inlet manifold 68 and a diagonally located side closedmanifold 70. All external manifolds are integral and contiguous withfin plate 10. Although external manifolds are shown with retangular geometries, any geometry capable of transferring fluid to and from the fin plate will work. - Referring now to 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 asfin plate 62; however,fin plate 63 additionally comprises closed endauxiliary manifold 64, open endauxiliary manifold 66, two pairs of interior side manifolds 68, 70, and a pair ofinterior inlets 65. Each pair of interior side manifolds comprise aside inlet manifold 68 and a diagonally located side closedmanifold 70. - Referring now to Fig. 6c, there is shown a perspective view of another embodiment of the interiorly manifolded fin plate generally designated 67.
Fin plate 67 is basically the same asfin plate 63. However,fin plate 67 comprises: oneinterior corner inlet 69; and one pair of interior corner manifolds wherein each pair comprises, one interior corner inlet manifold 71 positioned at theinterior corner inlet 69, and one interiorcorner outlet manifold 73 positioned on the same side as inlet manifold 71 but on the opposite end ofplate 67. As a heat exchange fluid entersfin plate 67, it flows through open manifold 71 andinlet 69, across internal flow guides 75, downchannels 77 defined byfins 79, acrossopen end port 81 and out through interiorcorner outlet manifold 73. It should be noted that flow guides 75 are similar tomanifold fins 28 and serve the same structural and thermodynamic purposes except that as the manifold run increases in length themanifold flow channels 83 increase in width. This design will provide optimum flow distribution across the face ofplate 67. - Another flow guide 75 configuration which would provide optimum flow distribution across the
fin plate 67,' Fig. 6d, entails the use of flow guides 75 designed to feedindividual channels 77 by having the flow guides 75 integrally connect withfins 79. As with the set of flow guides depicted in Fig. 6c, the spacing 83 between flow guides 75 will increase as the length of the run tofins 79 andchannels 77 increases. A pair oftab manifolds fin plate 67. The tab manifolds 85 and 87 provide the necessary continuous flow passages forfin plates 67 when they are stacked in an opposed manner in alternating sequence. - Referring now to Figs. 7a and 7b, and Figs. 8a, 8b and 8c, there are shown various views of an internally manifolded fin plate and
plate stack assembly 72. In the preferred operating condition, fin plates are stacked in an opposed manner in alternating'sequence. A first fluid is conveyed toinlet side manifold 68 wherein said fluid flows in throughside port 14 along the internal manifolding means 16 and is turned to flow downchannels 20 formed byfins 22. This first fluid then flows outend port 24 and into the open endauxiliary manifold 66. From theauxiliary 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 respectiveside inlet manifold 68. Then, similarly to the flow of the first fluid, the second fluid is conveyed in throughentry port 14 along theinternal manifold 16, downchannels 20 and alongfins 22. From there the second fluid exits into its respective open endsecondary manifold 66 where it would be conveyed to any appropriate location. Closed endsecondary manifolds 64 and side closedmanifolds 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. Furthermore, heat exchange fluids may be liquids or gases or combinations of liquids and gases. - Referring now to Fig. 9a, there is shown another embodiment of the internally and secondarily manifolded open-faced fin plate.
Fin plates annular structure 72. It should be noted that although the most preferredannular structure 72 is circular, any regular, even-number-sided, annular geometric structure will be preferred, and any annular geometric structure.will fall within the scope of the present invention. Representative annular structures include a square, a hexagon, an octagon, etc. Although in its most preferred form there are six interlocking fin plates, this system would work equally well with one or more fin plates. Additionally, some fin plates may not even carry a fluid but may serve as spacers and the like. In its preferred embodiment,annular structure 72 comprises at least oneoutlet fin plate 74 and oneinlet fin plate 76. In operation;a first fluid flows throughside inlet manifold 82, in throughside port 84, along the internal manifolding means 86 and is turned to flow alongchannels 88 formed byfins 90. This first fluid then flows outend port 92 on the outer periphery and into the opensecondary manifold area 78 where any collecting means will suffice. The first fluid is then conveyed to any appropriate location. A second fluid either warmer or colder than the first fluid is conveyed into theadjacent fin plate 76 by flowing throughside inlet manifold 94, throughside port 96, along theinternal manifold 98, and alongchannels 100 formed byfins 102. From there the second fluid exits throughexit port 104 on the inner periphery and into its respective open endsecondary manifold 80. In this particular embodiment, Fig. 9b shows a cutaway of an internally manifolded plate stack for generating countercurrent flow. This flow is obtained by alternately superposingfin plate 74 on top offin plate 76. Any number ofannular structures 72 may be stacked depending upon the desired capacity of the heat exchanger. To complete the stack of annular structures, a ring structure-shaped cover plate is sealably connected to the top annular structure of the internally manifolded annular plate stack. It should be noted that the cover plate can merely be another heat transferannular structure 72. Then, any conventional means for conveying the heat transfer fluid to and from a plate/fin-type heat exchanger is attached. Fig. 9c is an enlarged fragmentary perspective view showing approximate relative proportions of fins and channels. - In its preferred operating conditions,
annular structure 72 is made from a plurality of annular segments. In other operating conditions, the ring structure could be of unibody construction and designed to carry one or many fluids. Additionally, the annular stack may be designed to rotate along its axis if the specific design parameters indicated its desirability. - Referring now to Fig. 10a, there is shown another embodiment of the internally and interiorly manifolded open-faced fin plate. It should be noted that although
annular fin plate 106 is circular, any regular annular geometric- shaped plate will fall within the scope of the present invention. Althoughannular structure 72 is similar tofin plate 106, it should be noted thatstructure 72 is made up of a plurality of fin plate segments. In contrast to that,fin plate 106 of Fig. 10a is a unibody outlet plate. In operation, a first fluid flows throughinlet aperture 108 and along the internal manifolding means 110. From there,the first fluid is turned to flow alongchannels 112 formed byfins 114. This first fluid then flows outend port 116 on the outer periphery and into an opensecondary manifold area 118.Interior port 120 is located within the outer periphery ofoutlet fin plate 106 so as to provide means for channeling the second fluid to the alternating plate. Referring now to Fig. lOb, there is shown aninlet fin plate 122. A second fluid, either warmer or colder than the first fluid, is conveyed intofin plate 122 throughaperture 120. From there, the second fluid flows alongmanifold 124 and is turned to flow downchannels 126 formed byfins 128. From there, the second fluid exits throughexit ports 130 on the inner periphery and into its respective open endsecondary manifold area 132.Interior port 108 is located within the inner periphery offin plate 122 so as to provide means for channeling the first fluid to the alternating plate. In this particular embodiment an internally manifolded plate stack of annular configuration is obtained by superposinginlet fin plate 122 andoutlet fin plate 106 in alternating sequence to form the desired plate stack height. It should be noted that a plurality of inlets and outlets may be located within each plate if desired. To complete the plate stack, a ring structure-shaped cover plate is sealably connected to the top plate of the internally manifolded annular plate stack. It should be noted that the cover plate can merely be - another annular plate or it may be a solid plate. Then, any conventional means for conveying the heat transfer fluid to and from a plate/fin-type heat exchanger can be attached. - Depending upon the ultimate use and the desired heat transfer rate, 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, and not by way of limitation: metals, ceramics, polymers, etc.
- 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. The following discussion outlines the basis of thermal superiority of the IMPS design over previous design approaches.
- The basic technical merit provided by the design, presented in Fig. 8c, is that it allows a fundamental counterflow heat exchange design with all working surfaces having equal AT to the adjacent surface. As can be seen, 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 Alfa-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. Any turbulence due to waviness, protuberances or roughness results in an inefficient pressure loss and an actual decrease in overall heat transfer. If heat exchanger compactness is basically desired, the heat exchange benefit of waviness, roughness, interrupted fins, etc., can be put into the IMPS design by coining, etching, milling, etc., at some expense to the flow pressure losses. The added advantage of a different groove size geometry with simple tooling changes becomes an added feature of the design. - The internal manifolding feature, as shown throughout the Figures, 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.
- Under normal circumstances, the best thermal efficiency is achieved with a good counterflow design. Fig. 11 shows a basic comparison of parallel, crossflow and counterflow designs. It is seen that the efficiency for the parallel flow approaches 50%, crossflow 80%, and counterflow up to 90%, with sufficient length. Since the majority of fin plate heat exchangers are crossflow types . because of manifolding reasons, the proposed design shows an initial 10-15% advantage on this basis alone.
- The ability to handle either the crossflow or parallel flow case is, however, not excluded with the IMPS design and, alternatively, the use of added cross counterflow fluids and paths is also allowed.
- Three distinct heat exchanger examples are shown in Figs. 12a, 12b, and 12c. All three designs represent counterflow designs which, as described, represent the best heat transfer efficiency approach.
- In Fig. 12a, for a corrugated or wave shape wall design, the effect of the waves will be to add turbulence which will enhance the heat transfer, but at great expense on the pressure drop due to aerodynamic head loss effects, rather than pure friction. As also shown, unless the surface alignment and spacing is equally matched between cold and hot side surfaces, correctly, inadvertent pressure loss and nonefficient heat transfer would occur. Moreover, no conduction between plate to plate in the assembly can occur in this design.
- In Fig. 12b, a counterflow ribbed fin plate is illustrated. It has the benefit of extended fin surfaces but not the effect of thermal conduction plate to plate. Moreover, the spacing of the passages is such that only low pressure differentials can be supported between plates and as a consequence, heat transfer rates vary from plate to plate and along and across any given plate surface area.
- The proposed plate stack design, Fig. 12c, heat exchanger provides for the optimum counterflow design together with extended surface finned construction and no corrugations (if minimum pressure loss is desired). Moreover, a principal advantage is the intimate thermal joint provided by the plate stack which provides for thermal improvements for (almost) all circumstances. For tall height passage designs where the heat transfer coefficients are small compared to the ratio of the material thermal conductivity to mean characteristics height (i.e., NBi≤ 1.0) the plate-to-plate contact will mean the benefit of the superior thermal conduction of the metal not only between two adjacent plates but from other plates far removed from the immediate thermal joint. In this manner, the added ability of the design to improve heat conduction, results from the three-. dimensional thermal conduction within the plate stack. Moreover, the better 3-D thermal conduction in the design also reduces the peak thermal stresses by the proportionate reduction in peak surface temperatures within the exchanger.
- The benefit of the plate-to-plate contact can be expressed by an enhancement ratio:
- Fig. 13 illustrates for the designs, the requirements of S' vs heat transfer coefficient. For all but the highest heat transfer rate conditions, a practical thickness can be found to use the IMPS plate stack approach.
- The overall heat transfer rate q/A for the plate stack heat exchanger on a unit surface area basis between plates may be expressed as (approximately):
-
-
-
- As a result, as shown in the next discussion, this bounds the theoretical heat exchange enhancement ratio limit.
- For various situations of cold and hot side heat transfer coefficients and materials and realistic geometries, the use of either
Equation 3 or exact computer solutions must be performed. - The maximum theoretical thermal enhancement ratio that can be provided by the plate stack approach may be seen in Fig. 14. The value φ represents the enhancement to be obtained by a high conductivity material (copper or silver) as an example. A value of φ = 1.0 represents a normal (e.g., tube in shell) baseline heat exchanger design. Added limit boundaries are shown for the theoretical best line and a (typical) manufacturing limit line. It is shown that typical values of 3 to 4 times the tube-in-shell heat transfer coefficients will occur with a typical design for the same heat transfer coefficient (equal pumping power). Values of φ at 10 times or greater the baseline heat exchange values can be foreseen under some projected circumstances with equal power loss.
- Fig. 15 illustrates for a particular example design recuperator geometry a plate stack computer design analysis with a nominal value of 1.4, i.e., 40% better than the tube-in-shell. As illustrated, the plate stack design can alternatively reduce the required cold side heat transfer coefficient to 50% of the tube-in-shell value (25% of original pumping power).
- For lower thermal conductivity materials, a degradation will occur in performance as shown in Fig. 16. For ϕ (degradation factor) values in the
range 0≤ψ≤0.1 a minimum degradation is shown. This implies the sizing of the plate stack heat exchanger to ensure the material chosen and the thickness values are satisfactory compared to the lowest heat transfer coefficient in the stack (cold or hot side). -
- These parameters are of importance for design of heat exchange rate, pumping power, and weight (cost) respectively, to assist in design detailing.
- Obviously, many modifications and variations of the present invention are possible in light of the above teachings. It is therefore to be understood that, within the scope of the appended claims, the invention may be practiced otherwise than as specifically described.
- What is new and is desired to be secured by letters patent of the United States is:
Claims (12)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE8282105574T DE3279938D1 (en) | 1982-06-24 | 1982-06-24 | A heat exchanger |
EP19820105574 EP0097726B1 (en) | 1982-06-24 | 1982-06-24 | A heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19820105574 EP0097726B1 (en) | 1982-06-24 | 1982-06-24 | A heat exchanger |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0097726A1 true EP0097726A1 (en) | 1984-01-11 |
EP0097726B1 EP0097726B1 (en) | 1989-09-13 |
Family
ID=8189100
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19820105574 Expired EP0097726B1 (en) | 1982-06-24 | 1982-06-24 | A heat exchanger |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0097726B1 (en) |
DE (1) | DE3279938D1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2580794A1 (en) * | 1985-04-23 | 1986-10-24 | Inst Francais Du Petrole | THERMAL EXCHANGE DEVICE USABLE IN PARTICULAR FOR EXCHANGES BETWEEN GASES |
EP0206067A1 (en) * | 1985-06-20 | 1986-12-30 | Stettner & Co. | Catalytic active structure comprising individual units and process for producing such units |
DE3522095A1 (en) * | 1985-06-20 | 1987-01-02 | Stettner & Co | Apparatus for treating flowing media, and method for the manufacture thereof |
WO1996029558A1 (en) * | 1995-03-17 | 1996-09-26 | Michael Rehberg | Plate heat exchanger |
EP2510288A1 (en) * | 2009-12-08 | 2012-10-17 | NY Kraft Sverige AB | Heat exchanger with guided air flows |
CN115183611A (en) * | 2022-09-08 | 2022-10-14 | 中国核动力研究设计院 | Heat exchange component |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE143252C (en) * | ||||
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 (en) * | 1977-02-15 | 1978-08-17 | Rosenthal Technik Ag | CERAMIC, RECUPERATIVE COUNTERFLOW HEAT EXCHANGER |
EP0044561A2 (en) * | 1980-07-21 | 1982-01-27 | MüANYAGIPARI KUTATO INTEZET | Heat exchanger, in particular for heat exchange between gaseous fluids |
-
1982
- 1982-06-24 EP EP19820105574 patent/EP0097726B1/en not_active Expired
- 1982-06-24 DE DE8282105574T patent/DE3279938D1/en not_active Expired
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE143252C (en) * | ||||
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 (en) * | 1977-02-15 | 1978-08-17 | Rosenthal Technik Ag | CERAMIC, RECUPERATIVE COUNTERFLOW HEAT EXCHANGER |
EP0044561A2 (en) * | 1980-07-21 | 1982-01-27 | MüANYAGIPARI KUTATO INTEZET | Heat exchanger, in particular for heat exchange between gaseous fluids |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2580794A1 (en) * | 1985-04-23 | 1986-10-24 | Inst Francais Du Petrole | THERMAL EXCHANGE DEVICE USABLE IN PARTICULAR FOR EXCHANGES BETWEEN GASES |
EP0202981A1 (en) * | 1985-04-23 | 1986-11-26 | Institut Français du Pétrole | Device for heat exchange, especially for use in gas heat exchanges |
EP0206067A1 (en) * | 1985-06-20 | 1986-12-30 | Stettner & Co. | Catalytic active structure comprising individual units and process for producing such units |
DE3522095A1 (en) * | 1985-06-20 | 1987-01-02 | Stettner & Co | Apparatus for treating flowing media, and method for the manufacture thereof |
WO1996029558A1 (en) * | 1995-03-17 | 1996-09-26 | Michael Rehberg | Plate heat exchanger |
US6085832A (en) * | 1995-03-17 | 2000-07-11 | Rehberg; Michael | Plate heat exchanger |
EP2510288A1 (en) * | 2009-12-08 | 2012-10-17 | NY Kraft Sverige AB | Heat exchanger with guided air flows |
EP2510288A4 (en) * | 2009-12-08 | 2014-06-25 | Ny Kraft Sverige Ab | Heat exchanger with guided air flows |
CN115183611A (en) * | 2022-09-08 | 2022-10-14 | 中国核动力研究设计院 | Heat exchange component |
CN115183611B (en) * | 2022-09-08 | 2022-11-18 | 中国核动力研究设计院 | Heat exchange component |
Also Published As
Publication number | Publication date |
---|---|
DE3279938D1 (en) | 1989-10-19 |
EP0097726B1 (en) | 1989-09-13 |
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