US20190086156A1 - Cross-flow plate heat and/or moisture exchanger - Google Patents
Cross-flow plate heat and/or moisture exchanger Download PDFInfo
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- US20190086156A1 US20190086156A1 US16/073,502 US201616073502A US2019086156A1 US 20190086156 A1 US20190086156 A1 US 20190086156A1 US 201616073502 A US201616073502 A US 201616073502A US 2019086156 A1 US2019086156 A1 US 2019086156A1
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- 239000012530 fluid Substances 0.000 claims abstract description 60
- 239000012528 membrane Substances 0.000 claims description 15
- 239000000463 material Substances 0.000 claims description 10
- 229920003023 plastic Polymers 0.000 claims description 6
- 239000004033 plastic Substances 0.000 claims description 6
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 3
- 229910052782 aluminium Inorganic materials 0.000 claims description 3
- 239000002861 polymer material Substances 0.000 claims description 3
- 229920002635 polyurethane Polymers 0.000 claims description 3
- 239000004814 polyurethane Substances 0.000 claims description 3
- 230000001154 acute effect Effects 0.000 claims description 2
- 238000010276 construction Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 2
- 229920000728 polyester Polymers 0.000 description 2
- 238000009434 installation Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
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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
- F28D9/0062—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 spaced plates with inserted elements
- F28D9/0068—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 spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
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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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0015—Heat and mass exchangers, e.g. with permeable walls
-
- 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
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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
- F28D9/02—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 heat-exchange media travelling at an angle to one another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
- F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow
Definitions
- the invention relates to a cross-flow plate heat and/or moisture exchanger having plates that are above, below or next to one another and form alternating flow passages for a first and a second fluid.
- the invention is based on the requirement to provide an improved cross-flow plate heat and/or moisture exchanger that on the one hand exhibits better transfer performance during the transfer of heat and/or moisture between the two fluids and that moreover has increased pressure stability in relation to differential pressures between the two fluid flows.
- each plate of the cross-flow plate heat and/or moisture exchanger has a first cross-flow region, a counter-flow region downstream of the first cross-flow region in flow direction and a second cross-flow region downstream of the counter-flow region in flow direction, in that the cross-flow regions of adjacent plates form flow passages running approximately perpendicular to each other, in that the counter-flow regions of adjacent plates form flow passages running approximately parallel to one another, in that the first or the second cross-flow region of each plate in terms of its dimensions corresponds to the second or first cross-flow region of each adjacent plate and is above, below or next to same, and in that the counter-flow region of each plate in terms of its dimensions corresponds to the counter-flow region of each adjacent plate and is above, below or next to same.
- the first cross-flow region of each plate causes the respective fluid flow to be evenly distributed across the counter-flow region of each plate. Due to the difference in design of the adjacent plates, these can mutually support each other very well, wherein nevertheless, in the area of the respective counter-flow regions, an approximately parallel progression of the respective flow passages is made possible.
- the counter-flow passages of the cross-flow region of each adjacent plate extend at a small acute angle of preferably 5 to 25°. This ensures an approximately parallel progression of the counter-flow passages formed by the adjacent plates in the adjacent flow passages, wherein moreover it is ensured that the adjacent plates are mechanically firmly supported against each other.
- turbulences can be initiated in the flows of the two fluids that can contribute to an improvement of the transfer conditions of heat and/or moisture right through the plates between the two fluids.
- the plates are shaped in the form of a rectangle or a square.
- the counter-flow regions of each plate are shaped as an approximate oval or ellipse extending between two opposing corners of the plate.
- the general flow direction A, B through the cross-flow plate heat and/or moisture exchanger, of the two fluids separated from each other by the plates is chosen such that the two fluids flow through the counter-flow regions of the cross-flow plate heat and/or moisture exchanger in counter direction, i.e. approximately anti-parallel.
- the flow conditions in the cross-flow regions of the cross-flow plate heat and/or moisture exchanger according to the invention are comparatively regular and orderly, which for certain requirement profiles on the cross-flow plate heat and/or moisture exchanger is convenient and advantageous.
- the requirement profiles for the cross-flow plate heat and/or moisture exchanger according to the invention are of a different kind, i.e. if more turbulent flow conditions are desired in the cross-flow regions thereof, it is convenient if walls of the flow passages of the cross-flow regions between the plates comprise interruptions.
- Particularly advantageous materials for the plates of the cross-flow plate heat and/or moisture exchanger according to the invention have proved to be aluminum and plastic, preferably PET plastic, in particular then, when the cross-flow plate heat and/or moisture exchanger according to the invention is to be used merely for temperature transfer between the two fluids.
- each membrane plate comprises a membrane layer and a support layer.
- enthalpy can be transferred between the two fluids.
- the at least one support layer is configured perforated.
- the membrane plate can be given a specifiable mechanical strength and a spatial structure, wherein both the mechanical strength and the spatial structure can be permanently maintained.
- the membrane layer of the plates is conveniently formed of a suitable plastic material, preferably a polyurethane or a polymer material.
- the support layer of the plates is conveniently formed of a suitable fleece material, preferably a polyester material.
- FIG. 1 shows an embodiment of a plate of the first design for a cross-flow plate heat and/or moisture exchanger according to the invention comprising two differently constructed plates;
- FIG. 2 shows an embodiment of a plate of the second design for a cross-flow plate heat and/or moisture exchanger according to the invention comprising two differently constructed plates;
- FIG. 3 shows a schematic diagram of a cross-flow plate heat and/or moisture exchanger according to the invention comprising embodiments of plates depicted in FIGS. 1 and 2 .
- a cross-flow plate heat and/or moisture exchanger 1 according to the invention shown in a schematic diagram in FIG. 3 consists of a plate packet composed of plates 2 , 3 of different design or construction.
- the plates 2 and the plates 3 are in an alternating manner, i.e. a plate 2 of the first construction type is followed respectively by a plate 3 of the second construction type.
- each plate 2 of the first construction type has two adjacent plates 3 of the second construction type and vice-versa.
- the plates 2 , 3 are on top of each other. It is, of course, possible to arrange the plates 2 , 3 adjacently to each other.
- the two sides of the plates 2 , 3 facing each other limit flow passages for a first fluid that flows through the cross-flow plate heat and/or moisture exchanger 1 of FIG. 1 in a general direction indicated by arrows A, and for a second fluid that flows through the cross-flow plate heat and/or moisture exchanger 1 of FIG. 2 in a general direction indicated by arrows B.
- the general direction A of the first fluid is approximately perpendicular to the general direction B of the second fluid.
- the flow passages for the first fluid and for the second fluid are in an alternating manner in the plate packet shown in FIG. 3 made up of plates 2 , 3 .
- the flow passages for the first fluid are determined by the design shown in FIG. 1 of the plate 2 of the first construction type.
- the flow passages for the second fluid are determined by the design shown in FIG. 2 for the plate 3 of the second construction type.
- the plates 2 , 3 of the cross-flow plate heat and/or moisture exchanger 1 may be made of any suitable material, for example aluminum or a PET material.
- the plates 2 , 3 of the cross-flow plate heat and/or moisture exchanger 1 are configured as membrane plates.
- the respective membrane plates consist of a membrane layer by means of which enthalpy can be transferred between the two fluids, and at least one perforated support layer by means of which a specifiable mechanical strength and a spatial structure can be imparted to the membrane plate and be maintained therein.
- the membrane layer of plates 2 , 3 is then formed from a suitable plastic material, in particular a polyurethane or a polymer material.
- the support layer of the plates 2 , 3 is then formed from a suitable fleece material, preferably from a polyester fleece or similar.
- the flow passages that are provided in the cross-flow plate heat and/or moisture exchanger 1 for the first fluid are designed according to the structure of plate 2 of the first construction type as depicted in the following in FIG. 1 .
- the plate 2 has a first cross-flow region 4 , into which the first fluid enters.
- the first cross-flow region 4 comprises flow passages 5 extending in parallel, through which the first fluid is guided to a counter-flow region 6 downstream of the first cross-flow region 4 .
- the counter-flow region 6 comprises a larger number of counter flow passages 7 in comparison to the number of flow passages 5 of the first cross-flow region 4 .
- the counter-flow passages 7 are at an incline to the flow passages 5 .
- the counter-flow passages 7 as from a certain length, comprise length portions of varying direction.
- the varying length of the counter-flow passages 7 stems from the fact that the counter-flow region 6 of the first plate 2 extends from the right upper corner 8 thereof in FIG. 1 to the left lower corner 9 thereof in FIG. 1 and comprises an elliptical or oval shape tapering in direction of the corners 8 , 9 .
- the first fluid is guided through the multiplicity of counter-flow passages 7 to a second cross-flow region 10 of the plate 2 .
- the second cross-flow region 10 comprises flow passages 11 that extend in parallel to the flow passages 5 of the first cross-flow region 4 and that respectively extend in the general direction A, in which the first fluid flows through the cross-flow plate heat and/or moisture exchanger 1 .
- the flow passages that are provided in the cross-flow plate heat and/or moisture exchanger 1 for the second fluid are designed according to the structure of plate 3 of the second construction type as depicted in the following in FIG. 2 .
- the plate 3 has a first cross-flow region 12 , into which the second fluid enters.
- the first cross-flow region 12 comprises flow passages 13 extending in parallel, through which the second fluid is guided to a counter-flow region 14 downstream of the first cross-flow region 12 .
- the counter-flow region 14 comprises a larger number of counter flow passages 15 in comparison to the number of flow passages 13 of the first cross-flow region 12 .
- the counter-flow passages 15 are at an incline to the flow passages 13 .
- the counter-flow passages 15 as from a certain length, comprise length portions of varying direction.
- the varying length of the counter-flow passages 15 stems from the fact that the counter-flow region 14 of the second plate 3 extends from the right upper corner 16 thereof in FIG. 2 to the left lower corner 17 thereof in FIG. 2 and comprises an elliptical or oval shape tapering in direction of the corners 16 , 17 .
- the second fluid is guided through the multiplicity of counter-flow passages 15 to a second cross-flow region 18 of the plate 3 .
- the second cross-flow region 18 comprises flow passages 19 that extend in parallel to the flow passages 13 of the first cross-flow region 12 and that respectively extend in the general direction B, in which the second fluid flows through the cross-flow plate heat and/or moisture exchanger 1 .
- the plate packet of the cross-flow plate heat and/or moisture exchanger 1 is constructed by arranging the differently constructed plates 2 , 3 depicted in FIG. 1 and FIG. 2 in an alternating manner on top of each other.
- the first cross-flow region 4 of plate 2 in terms of its layout and its dimensions, corresponds to plate 3 depicted in FIG. 2 .
- the second cross-flow region 10 of plate 2 depicted in FIG. 1 in terms of its shape and its dimensions, corresponds to the first cross-flow region 12 of plate 3 depicted in FIG. 2 .
- the first fluid and the second fluid, in the cross-flow regions 4 , 10 , 12 , 18 of the two plates 2 , 3 flow in their general directions A or B and thus approximately perpendicular to each other.
- the plates 2 , 3 in the embodiments shown in FIGS. 1 and 2 are shaped approximately as a square. Since the contours and the layout of the cross-flow regions 4 and 18 / 10 and 12 of plates 2 , 3 correspond to each other, this also applies to the contours and the layout of the counter-flow regions 6 , 14 of the two plates 2 , 3 .
- the first fluid and the second fluid flow in an opposite or anti-parallel flow direction.
- the directional changes of the counter-flow passages 7 and 15 provided in the counter-flow regions 6 , 14 cause irregularities or turbulences of the flows of the first fluid and of the second fluid that contributes to an improvement in the heat and/or moisture transfer between the fluids 1 , 2 .
- the counter-flow passages 7 of the counter-flow region 6 of plate 2 are, in the case of plates 2 , 3 depicted in FIGS. 1 and 2 , inclined by a comparatively small angle that may be between 5° and 25°, in relation to the counter-flow passages 15 of the counter-flow region 14 of plate 2 .
- walls 20 of the flow passages 5 of the first cross-flow region 4 of plate 2 , walls 21 of the flow passages 11 of the second cross-flow region 10 of plate 2 , walls 21 of the flow passages 13 of the first cross-flow region 12 of plate 3 and walls 23 of flow passages 19 of the second cross-flow region 18 of plate 3 are constructed without interruptions, i.e. in a uniform and continuous manner. Interruptions between the said walls, in the case of plates 2 , 3 depicted in FIGS. 1 and 2 , exist in particular at the transitions between the cross-flow regions 4 , 10 , 12 , 18 and the counter-flow regions 6 , 14 .
- the walls of flow passages 5 , 11 , 13 , 19 may, of course, also have interruptions.
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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
- The invention relates to a cross-flow plate heat and/or moisture exchanger having plates that are above, below or next to one another and form alternating flow passages for a first and a second fluid.
- Based on the above-mentioned state of the art the invention is based on the requirement to provide an improved cross-flow plate heat and/or moisture exchanger that on the one hand exhibits better transfer performance during the transfer of heat and/or moisture between the two fluids and that moreover has increased pressure stability in relation to differential pressures between the two fluid flows.
- According to the invention this requirement is met in that each plate of the cross-flow plate heat and/or moisture exchanger has a first cross-flow region, a counter-flow region downstream of the first cross-flow region in flow direction and a second cross-flow region downstream of the counter-flow region in flow direction, in that the cross-flow regions of adjacent plates form flow passages running approximately perpendicular to each other, in that the counter-flow regions of adjacent plates form flow passages running approximately parallel to one another, in that the first or the second cross-flow region of each plate in terms of its dimensions corresponds to the second or first cross-flow region of each adjacent plate and is above, below or next to same, and in that the counter-flow region of each plate in terms of its dimensions corresponds to the counter-flow region of each adjacent plate and is above, below or next to same.
- Due to this design of the two differently constructed plates that are combined to form the cross-flow plate heat and/or moisture exchanger, it is achieved that the two fluids flowing through the cross-flow plate heat and/or moisture exchanger flow essentially anti-parallel to one another, as a result of which the efficiency of the cross-flow plate heat and/or moisture exchanger is considerably improved in comparison to corresponding aggregates known from the state of the art. Due to the flow passages running perpendicular to one another a mechanically stable design of the cross-flow plate heat and/or moisture exchanger is obtained. Since a counter-flow region is provided in each flow passage of the cross-flow plate heat and/or moisture exchanger according to the invention, it is ensured that the two fluids in this counter-flow region are guided past each other in an approximately anti-parallel manner. According to the invention it has become possible to steer the flow direction of the first fluid in direction of the entry of the second fluid so that the temperature or the moisture of the first fluid can move closer to the entry temperature or moisture of the second fluid. Similarly the temperature and/or the moisture of the second fluid can move closer to the entry temperature or moisture of the first fluid. By proceeding in this way high degrees of transfer are achievable that lie in the range of up to 90%.
- The first cross-flow region of each plate causes the respective fluid flow to be evenly distributed across the counter-flow region of each plate. Due to the difference in design of the adjacent plates, these can mutually support each other very well, wherein nevertheless, in the area of the respective counter-flow regions, an approximately parallel progression of the respective flow passages is made possible.
- In order to ensure that the stability of the plate packet of the cross-flow plate heat and/or moisture exchanger according to the invention also in the area of the counter-flow regions of the plates is of high quality even for the most varied pressures in the different fluids, it is advantageous if the counter-flow passages of the cross-flow region of each adjacent plate extend at a small acute angle of preferably 5 to 25°. This ensures an approximately parallel progression of the counter-flow passages formed by the adjacent plates in the adjacent flow passages, wherein moreover it is ensured that the adjacent plates are mechanically firmly supported against each other.
- When the direction of counter-flow passages of the counter-flow regions of the plates changes, turbulences can be initiated in the flows of the two fluids that can contribute to an improvement of the transfer conditions of heat and/or moisture right through the plates between the two fluids.
- In order to keep the installation cost for the cross-flow plate heat and/or moisture exchanger according to the invention to a minimum and in order to be able to ensure reliable sealing on the plate edges at a minimum of engineering effort, it is advantageous if the plates are shaped in the form of a rectangle or a square.
- According to an advantageous embodiment of the cross-flow plate heat and/or moisture exchanger according to the invention the counter-flow regions of each plate are shaped as an approximate oval or ellipse extending between two opposing corners of the plate.
- According to a further advantageous embodiment of the cross-flow plate heat and/or moisture exchanger according to the invention the general flow direction A, B through the cross-flow plate heat and/or moisture exchanger, of the two fluids separated from each other by the plates, is chosen such that the two fluids flow through the counter-flow regions of the cross-flow plate heat and/or moisture exchanger in counter direction, i.e. approximately anti-parallel.
- If walls of the flow passages of the cross-flow regions that are between the plates, are formed in a uniform or uninterrupted manner, the flow conditions in the cross-flow regions of the cross-flow plate heat and/or moisture exchanger according to the invention are comparatively regular and orderly, which for certain requirement profiles on the cross-flow plate heat and/or moisture exchanger is convenient and advantageous.
- If the requirement profiles for the cross-flow plate heat and/or moisture exchanger according to the invention are of a different kind, i.e. if more turbulent flow conditions are desired in the cross-flow regions thereof, it is convenient if walls of the flow passages of the cross-flow regions between the plates comprise interruptions.
- Particularly advantageous materials for the plates of the cross-flow plate heat and/or moisture exchanger according to the invention have proved to be aluminum and plastic, preferably PET plastic, in particular then, when the cross-flow plate heat and/or moisture exchanger according to the invention is to be used merely for temperature transfer between the two fluids.
- If the cross-flow plate heat and/or moisture exchanger according to the invention is to be used also or predominantly for moisture or enthalpy exchange between the two fluids, it is advantageous if the plates are configured as membrane plates. In this case each membrane plate comprises a membrane layer and a support layer. By means of the membrane layer enthalpy can be transferred between the two fluids. The at least one support layer is configured perforated. By means of the perforated support layer the membrane plate can be given a specifiable mechanical strength and a spatial structure, wherein both the mechanical strength and the spatial structure can be permanently maintained.
- The membrane layer of the plates is conveniently formed of a suitable plastic material, preferably a polyurethane or a polymer material.
- The support layer of the plates is conveniently formed of a suitable fleece material, preferably a polyester material.
- The invention will now be described in detail by way of an embodiment with reference to the drawing, in which
-
FIG. 1 shows an embodiment of a plate of the first design for a cross-flow plate heat and/or moisture exchanger according to the invention comprising two differently constructed plates; -
FIG. 2 shows an embodiment of a plate of the second design for a cross-flow plate heat and/or moisture exchanger according to the invention comprising two differently constructed plates; and -
FIG. 3 shows a schematic diagram of a cross-flow plate heat and/or moisture exchanger according to the invention comprising embodiments of plates depicted inFIGS. 1 and 2 . - A cross-flow plate heat and/or moisture exchanger 1 according to the invention shown in a schematic diagram in
FIG. 3 consists of a plate packet composed of plates 2, 3 of different design or construction. Within the plate packet the plates 2 and the plates 3 are in an alternating manner, i.e. a plate 2 of the first construction type is followed respectively by a plate 3 of the second construction type. Accordingly each plate 2 of the first construction type has two adjacent plates 3 of the second construction type and vice-versa. In the case of the embodiment shown inFIG. 3 , the plates 2, 3 are on top of each other. It is, of course, possible to arrange the plates 2, 3 adjacently to each other. - The two sides of the plates 2, 3 facing each other limit flow passages for a first fluid that flows through the cross-flow plate heat and/or moisture exchanger 1 of
FIG. 1 in a general direction indicated by arrows A, and for a second fluid that flows through the cross-flow plate heat and/or moisture exchanger 1 ofFIG. 2 in a general direction indicated by arrows B. The general direction A of the first fluid is approximately perpendicular to the general direction B of the second fluid. - The flow passages for the first fluid and for the second fluid are in an alternating manner in the plate packet shown in
FIG. 3 made up of plates 2, 3. - The flow passages for the first fluid are determined by the design shown in
FIG. 1 of the plate 2 of the first construction type. The flow passages for the second fluid are determined by the design shown inFIG. 2 for the plate 3 of the second construction type. - The plates 2, 3 of the cross-flow plate heat and/or moisture exchanger 1 may be made of any suitable material, for example aluminum or a PET material.
- If the cross-flow plate heat and/or moisture exchanger 1 is also to be used essentially for moisture or enthalpy exchange between the two fluids that flow through same, the plates 2, 3 of the cross-flow plate heat and/or moisture exchanger 1 are configured as membrane plates. The respective membrane plates consist of a membrane layer by means of which enthalpy can be transferred between the two fluids, and at least one perforated support layer by means of which a specifiable mechanical strength and a spatial structure can be imparted to the membrane plate and be maintained therein.
- The membrane layer of plates 2, 3 is then formed from a suitable plastic material, in particular a polyurethane or a polymer material.
- The support layer of the plates 2, 3 is then formed from a suitable fleece material, preferably from a polyester fleece or similar.
- The flow passages that are provided in the cross-flow plate heat and/or moisture exchanger 1 for the first fluid, are designed according to the structure of plate 2 of the first construction type as depicted in the following in
FIG. 1 . In case of the embodiment shown inFIG. 1 the plate 2 has a first cross-flow region 4, into which the first fluid enters. The first cross-flow region 4 comprises flow passages 5 extending in parallel, through which the first fluid is guided to a counter-flow region 6 downstream of the first cross-flow region 4. In the embodiment shown the counter-flow region 6 comprises a larger number of counter flow passages 7 in comparison to the number of flow passages 5 of the first cross-flow region 4. The counter-flow passages 7 are at an incline to the flow passages 5. Moreover the counter-flow passages 7, as from a certain length, comprise length portions of varying direction. The varying length of the counter-flow passages 7 stems from the fact that the counter-flow region 6 of the first plate 2 extends from the right upper corner 8 thereof inFIG. 1 to the left lower corner 9 thereof inFIG. 1 and comprises an elliptical or oval shape tapering in direction of the corners 8, 9. - The first fluid is guided through the multiplicity of counter-flow passages 7 to a
second cross-flow region 10 of the plate 2. Thesecond cross-flow region 10 comprisesflow passages 11 that extend in parallel to the flow passages 5 of the first cross-flow region 4 and that respectively extend in the general direction A, in which the first fluid flows through the cross-flow plate heat and/or moisture exchanger 1. - The flow passages that are provided in the cross-flow plate heat and/or moisture exchanger 1 for the second fluid, are designed according to the structure of plate 3 of the second construction type as depicted in the following in
FIG. 2 . In case of the embodiment shown inFIG. 2 the plate 3 has afirst cross-flow region 12, into which the second fluid enters. Thefirst cross-flow region 12 comprisesflow passages 13 extending in parallel, through which the second fluid is guided to acounter-flow region 14 downstream of thefirst cross-flow region 12. In the embodiment shown thecounter-flow region 14 comprises a larger number ofcounter flow passages 15 in comparison to the number offlow passages 13 of thefirst cross-flow region 12. Thecounter-flow passages 15 are at an incline to theflow passages 13. Moreover thecounter-flow passages 15, as from a certain length, comprise length portions of varying direction. The varying length of thecounter-flow passages 15 stems from the fact that thecounter-flow region 14 of the second plate 3 extends from the rightupper corner 16 thereof inFIG. 2 to the leftlower corner 17 thereof inFIG. 2 and comprises an elliptical or oval shape tapering in direction of thecorners - The second fluid is guided through the multiplicity of
counter-flow passages 15 to asecond cross-flow region 18 of the plate 3. Thesecond cross-flow region 18 comprisesflow passages 19 that extend in parallel to theflow passages 13 of thefirst cross-flow region 12 and that respectively extend in the general direction B, in which the second fluid flows through the cross-flow plate heat and/or moisture exchanger 1. - As already explained, the plate packet of the cross-flow plate heat and/or moisture exchanger 1 is constructed by arranging the differently constructed plates 2, 3 depicted in
FIG. 1 andFIG. 2 in an alternating manner on top of each other. As can be seen inFIG. 1 andFIG. 2 , the first cross-flow region 4 of plate 2, in terms of its layout and its dimensions, corresponds to plate 3 depicted inFIG. 2 . Analogously the secondcross-flow region 10 of plate 2 depicted inFIG. 1 , in terms of its shape and its dimensions, corresponds to the firstcross-flow region 12 of plate 3 depicted inFIG. 2 . The first fluid and the second fluid, in thecross-flow regions - The plates 2, 3 in the embodiments shown in
FIGS. 1 and 2 are shaped approximately as a square. Since the contours and the layout of thecross-flow regions 4 and 18/10 and 12 of plates 2, 3 correspond to each other, this also applies to the contours and the layout of thecounter-flow regions 6, 14 of the two plates 2,3. - In the
counter-flow regions 6 and 14 the first fluid and the second fluid flow in an opposite or anti-parallel flow direction. The directional changes of thecounter-flow passages 7 and 15 provided in thecounter-flow regions 6, 14 cause irregularities or turbulences of the flows of the first fluid and of the second fluid that contributes to an improvement in the heat and/or moisture transfer between the fluids 1, 2. - The general flow direction of fluid 1 in the counter-flow region 6 as well as of fluid 2 in the
counter-flow region 14, with the plates 2, 3 shown inFIGS. 1 and 2 , occurs at an angle of approximately 45° to the general directions A and B of fluid 1 and fluid 2, respectively. The counter-flow passages 7 of the counter-flow region 6 of plate 2 are, in the case of plates 2, 3 depicted inFIGS. 1 and 2 , inclined by a comparatively small angle that may be between 5° and 25°, in relation to thecounter-flow passages 15 of thecounter-flow region 14 of plate 2. This ensures that the mechanical structure of the plate packet forming the cross-flow plate heat and/or moisture exchanger 1 is stable with the distances between plates 2, 3 remaining unchanged even in the area of theircounter-flow regions 6, 14. When assembling the plate packet of the above-described cross-flow plate heat and/or moisture exchanger 1 it must be ensured that the entry section associated with the first fluid and the entry section associated with the second fluid are in relation to one another in such a way that the first and the second fluid flow in opposite directions in thecounter-flow regions 6, 14. - In the exemplary embodiment shown
walls 20 of the flow passages 5 of the first cross-flow region 4 of plate 2, walls 21 of theflow passages 11 of the secondcross-flow region 10 of plate 2, walls 21 of theflow passages 13 of the firstcross-flow region 12 of plate 3 and walls 23 offlow passages 19 of the secondcross-flow region 18 of plate 3 are constructed without interruptions, i.e. in a uniform and continuous manner. Interruptions between the said walls, in the case of plates 2, 3 depicted inFIGS. 1 and 2 , exist in particular at the transitions between thecross-flow regions counter-flow regions 6, 14. - Where more turbulent flow conditions are desired or necessary in the
cross-flow regions flow passages
Claims (13)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2016/000227 WO2017137054A1 (en) | 2016-02-11 | 2016-02-11 | Cross-flow plate heat and/or moisture exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20190086156A1 true US20190086156A1 (en) | 2019-03-21 |
Family
ID=55453113
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/073,502 Abandoned US20190086156A1 (en) | 2016-02-11 | 2016-02-11 | Cross-flow plate heat and/or moisture exchanger |
Country Status (7)
Country | Link |
---|---|
US (1) | US20190086156A1 (en) |
EP (1) | EP3414508B1 (en) |
CA (1) | CA3014091A1 (en) |
ES (1) | ES2770318T3 (en) |
PL (1) | PL3414508T3 (en) |
RU (1) | RU2018130819A (en) |
WO (1) | WO2017137054A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220153456A1 (en) * | 2020-11-13 | 2022-05-19 | Hamilton Sundstrand Corporation | Integrated condensing heat exchanger and water separator |
US20220163272A1 (en) * | 2017-05-18 | 2022-05-26 | Kai Klingenburg | Heat-exchanger plate |
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GB1339542A (en) * | 1970-03-20 | 1973-12-05 | Apv Co Ltd | Plate heat exchangers |
US4678030A (en) * | 1985-06-06 | 1987-07-07 | Reheat Ab | Plate heat exchanger |
US20100287953A1 (en) * | 2007-09-14 | 2010-11-18 | John Francis Urch | Air Conditioning Apparatus |
US8157000B2 (en) * | 2003-05-06 | 2012-04-17 | Meggitt (Uk) Ltd. | Heat exchanger core |
US8293416B2 (en) * | 2006-04-25 | 2012-10-23 | Panasonic Corporation | Fuel cell system |
US9287574B2 (en) * | 2011-09-21 | 2016-03-15 | Panasonic Intellectual Property Management Co., Ltd. | Polymer electrolyte fuel cell and fuel cell system including the same |
US10415900B2 (en) * | 2013-07-19 | 2019-09-17 | Westwind Limited | Heat / enthalpy exchanger element and method for the production |
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Publication number | Priority date | Publication date | Assignee | Title |
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US4347896A (en) * | 1979-10-01 | 1982-09-07 | Rockwell International Corporation | Internally manifolded unibody plate for a plate/fin-type heat exchanger |
LT5511B (en) * | 2007-08-21 | 2008-08-25 | Edvardas RAČKAUSKAS | Heat exchanger |
US20140076527A1 (en) * | 2012-09-20 | 2014-03-20 | Airia Leasing Inc. | Planar plate core and method of assembly |
JP2014134324A (en) * | 2013-01-09 | 2014-07-24 | Daikin Ind Ltd | Total enthalpy heat exchanger |
-
2016
- 2016-02-11 CA CA3014091A patent/CA3014091A1/en not_active Abandoned
- 2016-02-11 US US16/073,502 patent/US20190086156A1/en not_active Abandoned
- 2016-02-11 WO PCT/EP2016/000227 patent/WO2017137054A1/en active Application Filing
- 2016-02-11 PL PL16707626T patent/PL3414508T3/en unknown
- 2016-02-11 EP EP16707626.4A patent/EP3414508B1/en active Active
- 2016-02-11 RU RU2018130819A patent/RU2018130819A/en not_active Application Discontinuation
- 2016-02-11 ES ES16707626T patent/ES2770318T3/en active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1339542A (en) * | 1970-03-20 | 1973-12-05 | Apv Co Ltd | Plate heat exchangers |
US4678030A (en) * | 1985-06-06 | 1987-07-07 | Reheat Ab | Plate heat exchanger |
US8157000B2 (en) * | 2003-05-06 | 2012-04-17 | Meggitt (Uk) Ltd. | Heat exchanger core |
US8293416B2 (en) * | 2006-04-25 | 2012-10-23 | Panasonic Corporation | Fuel cell system |
US20100287953A1 (en) * | 2007-09-14 | 2010-11-18 | John Francis Urch | Air Conditioning Apparatus |
US9287574B2 (en) * | 2011-09-21 | 2016-03-15 | Panasonic Intellectual Property Management Co., Ltd. | Polymer electrolyte fuel cell and fuel cell system including the same |
US10415900B2 (en) * | 2013-07-19 | 2019-09-17 | Westwind Limited | Heat / enthalpy exchanger element and method for the production |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220163272A1 (en) * | 2017-05-18 | 2022-05-26 | Kai Klingenburg | Heat-exchanger plate |
US20220153456A1 (en) * | 2020-11-13 | 2022-05-19 | Hamilton Sundstrand Corporation | Integrated condensing heat exchanger and water separator |
Also Published As
Publication number | Publication date |
---|---|
EP3414508B1 (en) | 2019-11-13 |
CA3014091A1 (en) | 2017-08-17 |
ES2770318T3 (en) | 2020-07-01 |
WO2017137054A1 (en) | 2017-08-17 |
PL3414508T3 (en) | 2020-05-18 |
RU2018130819A (en) | 2020-03-11 |
EP3414508A1 (en) | 2018-12-19 |
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