CA1140530A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- CA1140530A CA1140530A CA000368783A CA368783A CA1140530A CA 1140530 A CA1140530 A CA 1140530A CA 000368783 A CA000368783 A CA 000368783A CA 368783 A CA368783 A CA 368783A CA 1140530 A CA1140530 A CA 1140530A
- Authority
- CA
- Canada
- Prior art keywords
- plates
- heat exchanger
- corrugations
- plate
- media
- 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
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
HEAT EXCHANGER
Abstract of The Disclosure In a heat exchanger comprising a plurality of plates arranged adjacent to each other and provided with turbulence-generating corrugations, sealed passages for two heat exchanging media are enclosed between the plates, and two heat exchanging media flow through the passages in mutually inclined flow direc-tions. In order to provide different thermal properties of the passages for the two media, the corrugations on an average extend at a wider angle relative to the flow direction of one of the media than to that of the other medium.
Abstract of The Disclosure In a heat exchanger comprising a plurality of plates arranged adjacent to each other and provided with turbulence-generating corrugations, sealed passages for two heat exchanging media are enclosed between the plates, and two heat exchanging media flow through the passages in mutually inclined flow direc-tions. In order to provide different thermal properties of the passages for the two media, the corrugations on an average extend at a wider angle relative to the flow direction of one of the media than to that of the other medium.
Description
'~LL~5~
The Dl closure The present invention relates to a heat exchanger of the type comprising a plurality of generally rectanyular plates arranged adjacent to each other and provided with turbulence-generating corrugations, said plates enclosing sealed passages for receiving two heat exchanging nedia flowing therethrough in mutually incllnecl flow directions.
By arranging the corruga-tions of adjacent plates in-clined to each other, a large number of supporting points are ~rovided in which the ridges of adjacent platcs abùt. In known heat exchangers of this kind, the corrugations are usually ar-ranged in a so-called herrincJbolle pattern, which means tllat the riclges and grooves orming the corrugations are brokcn along the lonc3itudinal axis of the plate and on both sides of s.lid a~is cx-tend at the sal~le an(Jle thcrcto. In this type of p]ate, the anc31e between the corrugations oE adjacent plates is providecl by rotating every other plate 180 in its own plane.
~' 0~3~1 The symmetrical corruga-tions of the plates of these known heat exchangers provide for equal thermal properties of all the heat exchanging passages. This is the case even when two different kinds of plates are used alternatively, i.e., plates having differing angles of corrugation. What has been said above applies even for diagonal flow, whlch means -that each of the heat exchanglng media flows between openings provided at dl-agonally opposite corners of the plates.
It is often deslrable to provlde heat exchanglng passages having different thermal properties for the two heat ex-changlng media in order to fulfill different objectives of heat exchange ln the most efficient manner. A proposed solution for attainlng this purpose is to provide alternate plates in the heat exchanger with a corrugation that is asymmetrlcal wi-th ~espect to the central plane o the plate, so that the grooves have a larger volume on one side of the plate than on the other. In this way, it is possible to provide a heat exchanger ln whlch the passages for the two media have different volumes and consequently differing thermal properties. However, -this known solution is disadvantageous ln that the corrugation cannot be effectively deslgned wlth regard to turbulence generation as well as pressure reslstance.
The present lnvention has for its principal object to provide different thermal properties of the passages for the two heat exchanging media without any reduction of the turbulence-generating capacity or mechanical strength of the corrugations.
This has been obtained by a heat exchanger of the first-men-tioned kind which is generally characterized in that the cor-rugations ex-tend in such directions that they form on an average a wider angle with the flow direction of one of the media than with -tha-t of the other, whereby the passages for -the two media provide mutually difering flow resistances.
The invention will be described in more detail below with reference to the accompanying drawings, in which Fig. 1 is an exploded, diagrammatical perspective view of a conventional plate heat exchanger, Fig. 2 is a corresponding view of an embodi-ment o the heat exchanger according to the invention, and Figs.
3-6 are diagrammatical plan views of preferred embodiments of heat exchanging plates to be used in the heat exchanger according to the invention.
The heat exchanger shown in Fig. 1 comprises a series of plates 1 and 2 arranged alternately and which are to be clamped together in a conventional manner in a frame-work which, for the sake of simplicity, has been omitted in the drawing. Two heat exchanging media A and B are conveyed via openings 3 and ~, respectively, to and from the heat exchanging passages formed be-tween the plates, as is indicated by dashed lines. As can be seen, the inlet and outlet openings for each medium are disposed at diagonally opposite corners of the plates, whereby the flow directions of the media A and B are mutually inclined.
The plates 1 and 2 in Fig. 1 are provided with corru-gations in a so-called herringbone pattern, as indicated at 6.
The corrugation creases extend at the same angle a relative to the longitudinal axls 5 of the plates on both sides of said axis.
To provide a mutual angle between the corrugat:ions of adjacent plates, alternate plates are rotated 180 in their own planes.
It is obvious that in a heat exchangQr assembled from plates 1 and 2 as defined above, which are completely symmetrical with regard to their longitudinal axis, all the heat exchanging passages will have identical thermal properties.
e__ _ 114~531~ ~
The heat exchanger according to the invention (Fig. 2) comprises a series of plates 11 and 1~ shown on a larger scale in Fig. 3. The heat exchanging media A and B are conveyed to and from the heat exchanging passages via openinys 13 and 14, respec-tively, situated at diagonally opposite corners of the plates.
As in Fig. 1, the heat exchange thus ta]ces place in cross~flow.
The plates are provlded with gaskets 18 as usual. The plates are further provided with corrugations in a herringbone pattern, the breaking line of which coincides with the longitudinal axis 15 of the plates. This "breaking line" is an imaginary line extending through the apices of the herringbones, where their two legs are joined. The diagrammatically indicated corrugation creases 16 and 17 are inclined to the longitudinal axis 15 at angles b and c, respectively, the angle c being considerably wider than the angle b. With the exception of the gasket arrangement 18, the plates 11 and 12 are ide~tical, alternate plates being rotated 180 in their own planes.
By comparison of the angles of the corrugations with the flow directions of the media A and B through the heat exchang-ing passages, it is found that medium A meets the corrugations ata considerably wider angle than medium B. Medium A, which flows between openings 13, thus has a flow direction generally trans-verse to the corrugations, while the flow direction of medium B
between openings 14 forms a relat-ively small angle with the corru-gations. The flow resistance is therefore considerably higher for medium A than for medium B, and the thermal properties of the passages for the two media are therefore considerably different from each other. The difference of thermal properties is because the angles b and c are different.
Figs. 4-6 illustrate further embodiments of heat ex-changing plates adapted to be arranged alternately in the same 11~0530 way as described above. The plates differ from those shown in Fig. 3 only wlth respect to the shape of the corrugation pattern, and therefore only this will be described.
The two plates 21 and 22 in Fig. 4 have identical corru-gations, alternate plates being turned :L80. In this case thecorrugation creases 23 and 24 are broken along a breaking line 26 and form angles d and e therewith, respectively. The breaking line 26 in turn forms an angle f with the longitudinal axis of the plate. The desired effect on the thermal properties of the passages accordlng to the invention is obtained provided that the corrugation creases 23 and 24 extend at different angles relative to the longitudinal axis 25.
Fig. 5 illustrates two plates 31 and 32 provided with unbroken corrugations 33 and 34 forming angles g and H, respec-tively, with the longitudinal axis 35. ~rovided that theseangles differ in width, the thermal properties of the heat ex-changing passages will be different.
Even the plates 41 and 42 shown in Fig. 6 are provided with unbroken corrugations 43 and 44 which on both plates form an angle 1 with the longitudinal axis 45. Since the corrugations in this case are parallel and thus will not cross and abut each other, supportiny points between the plates are instead provided in a known way by means of transverse ridges (not shown~ between the corrugation creases. It is easily realized that a passage extending between openings 46 (i.e., generally parallel to the corrugations) offers a considerably less flow resistance than a passage extending generally transverse to the corrugations between openlngs 47.
The plates in Fig. 6 are shown square. This makes it possible to obtain the biggest possible difference of thermal properties of the passages for the two media. This is because ~he flow directions of the media in this case form the widest ¦possible mutual angle (i.e., 90). With a corrugation arranyed as ¦in Fig. 6l one of the media will flow generally parallel to the ¦corrugation, which provides for the lowest possible flow re-S sistance, while the other medium will flow generally -transverse to the corruyation, which offers maximum flow resistance. By varying the angle 1, it is possible to adapt the thermal properties of the passages mutually as required. The difference is biggest when 1 is 45, as in Fig. 6, and is reduced towards zero when the angle approaches O or 90.
The square format can of course be used with a different corrugation pattern than that shown in Fig. 6.
A person skilled in the art will easily realize that other corrugation patterns than those describecl above are possible within the scope of the invention.
~, . . ~ ~
The Dl closure The present invention relates to a heat exchanger of the type comprising a plurality of generally rectanyular plates arranged adjacent to each other and provided with turbulence-generating corrugations, said plates enclosing sealed passages for receiving two heat exchanging nedia flowing therethrough in mutually incllnecl flow directions.
By arranging the corruga-tions of adjacent plates in-clined to each other, a large number of supporting points are ~rovided in which the ridges of adjacent platcs abùt. In known heat exchangers of this kind, the corrugations are usually ar-ranged in a so-called herrincJbolle pattern, which means tllat the riclges and grooves orming the corrugations are brokcn along the lonc3itudinal axis of the plate and on both sides of s.lid a~is cx-tend at the sal~le an(Jle thcrcto. In this type of p]ate, the anc31e between the corrugations oE adjacent plates is providecl by rotating every other plate 180 in its own plane.
~' 0~3~1 The symmetrical corruga-tions of the plates of these known heat exchangers provide for equal thermal properties of all the heat exchanging passages. This is the case even when two different kinds of plates are used alternatively, i.e., plates having differing angles of corrugation. What has been said above applies even for diagonal flow, whlch means -that each of the heat exchanglng media flows between openings provided at dl-agonally opposite corners of the plates.
It is often deslrable to provlde heat exchanglng passages having different thermal properties for the two heat ex-changlng media in order to fulfill different objectives of heat exchange ln the most efficient manner. A proposed solution for attainlng this purpose is to provide alternate plates in the heat exchanger with a corrugation that is asymmetrlcal wi-th ~espect to the central plane o the plate, so that the grooves have a larger volume on one side of the plate than on the other. In this way, it is possible to provide a heat exchanger ln whlch the passages for the two media have different volumes and consequently differing thermal properties. However, -this known solution is disadvantageous ln that the corrugation cannot be effectively deslgned wlth regard to turbulence generation as well as pressure reslstance.
The present lnvention has for its principal object to provide different thermal properties of the passages for the two heat exchanging media without any reduction of the turbulence-generating capacity or mechanical strength of the corrugations.
This has been obtained by a heat exchanger of the first-men-tioned kind which is generally characterized in that the cor-rugations ex-tend in such directions that they form on an average a wider angle with the flow direction of one of the media than with -tha-t of the other, whereby the passages for -the two media provide mutually difering flow resistances.
The invention will be described in more detail below with reference to the accompanying drawings, in which Fig. 1 is an exploded, diagrammatical perspective view of a conventional plate heat exchanger, Fig. 2 is a corresponding view of an embodi-ment o the heat exchanger according to the invention, and Figs.
3-6 are diagrammatical plan views of preferred embodiments of heat exchanging plates to be used in the heat exchanger according to the invention.
The heat exchanger shown in Fig. 1 comprises a series of plates 1 and 2 arranged alternately and which are to be clamped together in a conventional manner in a frame-work which, for the sake of simplicity, has been omitted in the drawing. Two heat exchanging media A and B are conveyed via openings 3 and ~, respectively, to and from the heat exchanging passages formed be-tween the plates, as is indicated by dashed lines. As can be seen, the inlet and outlet openings for each medium are disposed at diagonally opposite corners of the plates, whereby the flow directions of the media A and B are mutually inclined.
The plates 1 and 2 in Fig. 1 are provided with corru-gations in a so-called herringbone pattern, as indicated at 6.
The corrugation creases extend at the same angle a relative to the longitudinal axls 5 of the plates on both sides of said axis.
To provide a mutual angle between the corrugat:ions of adjacent plates, alternate plates are rotated 180 in their own planes.
It is obvious that in a heat exchangQr assembled from plates 1 and 2 as defined above, which are completely symmetrical with regard to their longitudinal axis, all the heat exchanging passages will have identical thermal properties.
e__ _ 114~531~ ~
The heat exchanger according to the invention (Fig. 2) comprises a series of plates 11 and 1~ shown on a larger scale in Fig. 3. The heat exchanging media A and B are conveyed to and from the heat exchanging passages via openinys 13 and 14, respec-tively, situated at diagonally opposite corners of the plates.
As in Fig. 1, the heat exchange thus ta]ces place in cross~flow.
The plates are provlded with gaskets 18 as usual. The plates are further provided with corrugations in a herringbone pattern, the breaking line of which coincides with the longitudinal axis 15 of the plates. This "breaking line" is an imaginary line extending through the apices of the herringbones, where their two legs are joined. The diagrammatically indicated corrugation creases 16 and 17 are inclined to the longitudinal axis 15 at angles b and c, respectively, the angle c being considerably wider than the angle b. With the exception of the gasket arrangement 18, the plates 11 and 12 are ide~tical, alternate plates being rotated 180 in their own planes.
By comparison of the angles of the corrugations with the flow directions of the media A and B through the heat exchang-ing passages, it is found that medium A meets the corrugations ata considerably wider angle than medium B. Medium A, which flows between openings 13, thus has a flow direction generally trans-verse to the corrugations, while the flow direction of medium B
between openings 14 forms a relat-ively small angle with the corru-gations. The flow resistance is therefore considerably higher for medium A than for medium B, and the thermal properties of the passages for the two media are therefore considerably different from each other. The difference of thermal properties is because the angles b and c are different.
Figs. 4-6 illustrate further embodiments of heat ex-changing plates adapted to be arranged alternately in the same 11~0530 way as described above. The plates differ from those shown in Fig. 3 only wlth respect to the shape of the corrugation pattern, and therefore only this will be described.
The two plates 21 and 22 in Fig. 4 have identical corru-gations, alternate plates being turned :L80. In this case thecorrugation creases 23 and 24 are broken along a breaking line 26 and form angles d and e therewith, respectively. The breaking line 26 in turn forms an angle f with the longitudinal axis of the plate. The desired effect on the thermal properties of the passages accordlng to the invention is obtained provided that the corrugation creases 23 and 24 extend at different angles relative to the longitudinal axis 25.
Fig. 5 illustrates two plates 31 and 32 provided with unbroken corrugations 33 and 34 forming angles g and H, respec-tively, with the longitudinal axis 35. ~rovided that theseangles differ in width, the thermal properties of the heat ex-changing passages will be different.
Even the plates 41 and 42 shown in Fig. 6 are provided with unbroken corrugations 43 and 44 which on both plates form an angle 1 with the longitudinal axis 45. Since the corrugations in this case are parallel and thus will not cross and abut each other, supportiny points between the plates are instead provided in a known way by means of transverse ridges (not shown~ between the corrugation creases. It is easily realized that a passage extending between openings 46 (i.e., generally parallel to the corrugations) offers a considerably less flow resistance than a passage extending generally transverse to the corrugations between openlngs 47.
The plates in Fig. 6 are shown square. This makes it possible to obtain the biggest possible difference of thermal properties of the passages for the two media. This is because ~he flow directions of the media in this case form the widest ¦possible mutual angle (i.e., 90). With a corrugation arranyed as ¦in Fig. 6l one of the media will flow generally parallel to the ¦corrugation, which provides for the lowest possible flow re-S sistance, while the other medium will flow generally -transverse to the corruyation, which offers maximum flow resistance. By varying the angle 1, it is possible to adapt the thermal properties of the passages mutually as required. The difference is biggest when 1 is 45, as in Fig. 6, and is reduced towards zero when the angle approaches O or 90.
The square format can of course be used with a different corrugation pattern than that shown in Fig. 6.
A person skilled in the art will easily realize that other corrugation patterns than those describecl above are possible within the scope of the invention.
~, . . ~ ~
Claims (6)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A plate heat exchanger comprising a plurality of generally rectangular plates arranged adjacent to each other and provided with turbulence-generating corrugations, said plates en-closing sealed heat exchanging passages for receiving two heat exchanging media flowing therethrough in mutually inclined flow directions, the heat exchanger being characterized in that said corrugations extend in such directions that they form on an average a wider angle with the flow direction of one of said media than with that of the other medium, whereby the passages for the two media provide different respective flow resistances.
2. The heat exchanger of claim 1, in which the plates are provided at their corner portions with inlet and outlet open-ings through which said media are conveyed to and from the heat exchanging passages, said inlet and outlet openings for each medium being provided at diametrically opposite corners of the plates.
3. The heat exchanger of claim 1, in which said plates have respective longitudinal axes, said corrugations of each plate being arranged in a herringbone pattern and on each side of a breaking line extending through the apices of the herring-bones, the corrugations on one side of said breaking line extend-ing at a different angle relative to the plate's longitudinal axis than the corrugations on the other side of said breaking line.
4. The heat exchanger of claim 3, in which said breaking line of each plate coincides with the longitudinal axis of the plate.
5. The heat exchanger of claim 3, in which said break-ing line of each plate is inclined to the longitudinal axis of the plate.
6. The heat exchanger of claim 1, in which the plates are generally square.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000368783A CA1140530A (en) | 1981-01-19 | 1981-01-19 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000368783A CA1140530A (en) | 1981-01-19 | 1981-01-19 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1140530A true CA1140530A (en) | 1983-02-01 |
Family
ID=4118952
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000368783A Expired CA1140530A (en) | 1981-01-19 | 1981-01-19 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1140530A (en) |
-
1981
- 1981-01-19 CA CA000368783A patent/CA1140530A/en not_active Expired
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |