EP2426453B1 - Elément d'échange thermique total - Google Patents

Elément d'échange thermique total Download PDF

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Publication number
EP2426453B1
EP2426453B1 EP09843988.8A EP09843988A EP2426453B1 EP 2426453 B1 EP2426453 B1 EP 2426453B1 EP 09843988 A EP09843988 A EP 09843988A EP 2426453 B1 EP2426453 B1 EP 2426453B1
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EP
European Patent Office
Prior art keywords
wave
form plate
heat exchange
plate member
total heat
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.)
Not-in-force
Application number
EP09843988.8A
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German (de)
English (en)
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EP2426453A1 (fr
EP2426453A4 (fr
Inventor
Masaru Takada
Hajime Sotokawa
Hidemoto Arai
Akira Doi
Takanori Imai
Kunihiko Kaga
Masaru Shinozaki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP2426453A1 publication Critical patent/EP2426453A1/fr
Publication of EP2426453A4 publication Critical patent/EP2426453A4/fr
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Publication of EP2426453B1 publication Critical patent/EP2426453B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • 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
    • F28D9/0062—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

Definitions

  • the present invention relates to a total heat exchange element in which a first fluid and a second fluid (e.g., air) are respectively caused to flow through a first flow passage and a second flow passage that are formed between plate members stacked in the manner of layers so as to extend in directions intersecting each other, so that a total heat exchange process is performed between the two fluids.
  • JP-A-02238293 discloses a total heat exchanger according to the preamble of claim 1.
  • partition members that separate the two fluids from each other and spacers that keep the partition members at an interval therebetween, as disclosed in, for example, Patent Literature 1.
  • the partition members have moisture permeability so that a heat exchange process is performed on sensible heat (temperature) and latent heat (humidity) at the same time between the two fluids while using the partition members as a medium. Because an object of such total heat exchange elements is to cause the fluids to perform a total heat exchange process, it is more desirable if the amount of heat exchanged in the element is larger.
  • Total heat exchange elements are more effective than commonly-used heat exchangers (that exchange only sensible heat), because the amount of heat exchanged thereby is larger by an amount corresponding to the exchanged latent heat.
  • cross-flow type There are two types of total heat exchange elements such as cross-flow type and counter-flow type.
  • the theoretical amount of exchanged heat per unit volume of the cross-flow type is smaller than that of the counter-flow type; however, the cross-flow type has advantages where, for example, the actual volume to be assembled into an apparatus is smaller, and also, the processing of the element itself is also easier, because the cross-flow type does not require a header (i.e., the part that divides the two fluids used for the total heat exchange process and that introduces the divided fluids into the total heat exchange element flow passages), which is structurally indispensable in the counter-flow type.
  • a header i.e., the part that divides the two fluids used for the total heat exchange process and that introduces the divided fluids into the total heat exchange element flow passages
  • the fins have an advantageous effect in the exchange of the sensible heat
  • the fins have no advantageous effect in the exchange of the latent heat.
  • the areas used for exchanging the latent heat are smaller.
  • improvements on the amount of exchanged heat that are especially realized by using fins are reaching a limit.
  • the diameters of pipes are small in relation to the flow rates of the fluids so that the flows are in a laminar-flow state where the Reynolds number thereof is smaller (approximately 100 to 1000) than those in other types of heat exchangers.
  • the advantageous effect of the improvements on the heat transfer coefficients realized by altering the flows of the fluids themselves is small.
  • fins and projections can rather be a cause of a problem where the pressure losses become larger, especially in the regions having a smaller Reynolds number. Having a larger pressure loss is not desirable because the energy consumption of a power device used for forwarding the fluids to the total heat exchange element becomes larger.
  • FIG. 8 is a schematic cross-sectional view for explaining a manner in which dead water regions occur in a flow passage.
  • dead water regions i.e., where the flows do not travel along the surfaces of the partition members and thus become stagnant
  • the heat transfer area size is, on the contrary, smaller in actuality.
  • the two surfaces of almost all the areas of the plate members being used have the mutually different fluids flow thereon, and also, the flow passages each have a shape that makes it difficult for dead water regions to occur.
  • substantially the entirety functions as an effective heat transfer area. Consequently, the heat transfer area size per unit volume is larger, and also, the amount of exchanged heat in the element is larger. Further, in the situation where it is acceptable to keep the amount of exchanged heat equal to that in the conventional example, it is possible to make, conversely, the volume of the element smaller. Thus, it is also possible to contribute to endeavors of saving resources.
  • first wave-form plate member, the second wave-form plate member, and the flat-plate-like member are configured by using the material having moisture permeability, it is possible to exchange not only the sensible heat but also the latent heat. Thus, an advantageous effect is achieved where it is possible to increase the amount of exchanged heat in the total heat exchange process.
  • FIG. 1 is a perspective view of a total heat exchange element according to a first embodiment of the present invention. To explain the embodiments clearly, the directions are supplementarily described while using the coordinate axes shown in the drawings; however, the present invention is not limited to this example.
  • a total heat exchange element 101 according to the first embodiment is configured so that a plurality of unit structuring members 20 each of which has flow passages formed therein are stacked in the manner of layers while being turned by 90 degrees for each of the layers.
  • Each of the unit structuring members 20 is configured with two wave-form plate members (i.e., a first wave-form plate member 11 and a second wave-form plate member 12) that are each shaped in the form of a wave and has moisture permeability and one flat-plate-like member 13 that has moisture permeability.
  • the total heat exchange element 101 is obtained by stacking, in the manner of layers, the plurality of unit structuring members 20 each of which is made up of the three plate members described above and further adding another flat-plate-like member 13 to an end in the layer stacking direction.
  • the first wave-form plate member 11 and the second wave-form plate member 12 are each substantially square and are shaped in the form of waves undulating in mutually the same cycle, by being folded in the thickness direction thereof (i.e., in the layer stacking direction, which is the Z-axis direction) from one side to the opposite side of the square (i.e., toward the direction of the Y-axis), so as to have a zigzag configuration in a cross-section thereof and so as to be generally in the form of the wave.
  • the first wave-form plate member 11 and the second wave-form plate member 12 that are shaped as described above are positioned while being apart from each other by a predetermined distance (i.e., a height of the flow passage) in the layer stacking direction (i.e., the Z-axis direction).
  • the first wave-form plate member 11 and the second wave-form plate member 12 are each processed into a size that matches the flat-plate-like member 13, when being projected onto a flat plane.
  • spacers 14 Interposed between the first wave-form plate member 11 and the second wave-form plate member 12 at both ends of the flow passages with respect to the width direction (i.e., both ends with respect to the X-axis direction) are spacers 14 each of which meanders in a zigzag configuration so as to fit the wave-like form, for the purpose of keeping the distance between the first wave-form plate member 11 and the second wave-form plate member 12 and for the purpose of hermetically closing both ends of the space between the first wave-form plate member 11 and the second wave-form plate member 12.
  • Each of the spacers 14 is hermetically fixed to the first wave-form plate member 11 and the second wave-form plate member 12 so that the flowing fluid (i.e., air in the present example) does not leak.
  • the flat-plate-like members 13 are positioned over the top and under the bottom with respect to the layer stacking direction of the first wave-form plate member 11 and the second wave-form plate member 12.
  • the upper flat-plate-like member 13 is the flat-plate-like member 13 added to the end described above.
  • the apexes (i.e., the ridges) of the wave-like forms of the first and the second wave-form plate members 11, 12 and the flat-plate-like member 13 are hermetically fixed to each other so that the flowing fluids do not leak.
  • straight flow passages (i.e., second flow passages) 32 each of which has a substantially triangular cross section are formed between each of the first and the second wave-form plate members 11, 12 and a corresponding one of the flat-plate-like members 13.
  • each of the unit structuring members 20 has formed therein the undulating flow passage 31 that has a rectangular cross section and that undulates in the layer stacking direction with respect to the traveling direction of the fluid; and the straight flow passages 32 each of which extends orthogonal to the undulating flow passage 31, has a substantially triangular cross section, and extends straight from the entrance to the exit thereof without meandering.
  • the plurality of unit structuring members 20 each of which is configured as described above are stacked in the manner of layers while being turned by 90 degrees for each of the layers, in such a manner that the directions of the waves intersect one another. In the example shown in FIG. 1 , three unit structuring members 20 are stacked in the manner of layers along the layer stacking direction (i.e., the Z-axis direction).
  • FIG. 2 is a perspective view for explaining the directions of the fluids flowing through the flow passages formed in the unit structuring members 20 positioned in the mutually different layers.
  • a first fluid A flowing in the X-axis direction from the right-hand side of FIG. 2 flows through the straight flow passages 32 in the first and the third layers (counted from the bottom) and through the undulating flow passage 31 in the second layer, as shown with a dashed arrow in the drawing.
  • the structure is arranged so that both the first fluid A and the second fluid B used for performing the heat exchange process on the sensible heat and the latent heat pass through the two mutually-different types of flow passages (i.e., the undulating flow passages 31 and the straight flow passages 32) at the same time.
  • the first fluid A and the second fluid B thus perform the heat exchange process, while using the first wave-form plate members 11, the second wave-form plate members 12, and the flat-plate-like members 13 as a medium having moisture permeability.
  • the flow passages that extend in the two mutually-different directions and through which the fluids used for performing the heat exchange process flow are made up of the two types of flow passages such as the undulating flow passages 31 and the straight flow passages 32 and are in mutually the same shapes, it is possible to arrange the pressure losses in both of the directions so as to be substantially equal.
  • FIG. 9 is a perspective view of an example of a conventional total heat exchange element shown for a comparison.
  • a total heat exchange element 201 shown in FIG. 9 is configured so that partition members 213 each of which is in the form of a flat plate and spacers (i.e., corrugated fins) 211 each of which is shaped in such a manner that the cross section thereof is in the form of corrugated fins are stacked in the manner of layers so as to alternate.
  • the layer stacking method being used can be explained as follows:
  • a unit structuring member 220 is prepared by positioning one partition member 213 and one spacer 211 on top of each other in such a manner that the projecting parts of the wave-like forms are in contact, as shown in FIG.
  • Unit structuring members 220 each prepared in this manner are stacked in the manner of layers so that the partition members 213 and the spacers 211 alternate and so that the directions in which the openings of the wave-like forms of the spacers 211 are oriented alternate by approximately 90 degrees. (In the example shown in FIG. 9 , six unit structuring members 220 are stacked in the manner of layers.) In the total heat exchange element 201, the first fluid A flowing in the X-axis direction from the right-hand side of FIG. 9 and the second fluid B flowing in the Y-axis direction from the left-hand side of FIG.
  • the first wave-form plate member 11 and the second wave-form plate member 12 according to the first embodiment function as a medium during the heat exchange process and correspond to the partition members 213 in the conventional example shown in FIG. 9 .
  • the most significant characteristic of the total heat exchange element according to the first embodiment is that the material is not wasted and that the heat transfer area size of the element per unit volume is kept large because almost all the wall surfaces within the element other than the spacers serve as direct heat-transfer areas having the mutually-different heat exchanging fluids flowing on the two surfaces thereof, instead of indirect heat-transfer areas like the fins. Because the fins transfer heat by giving the heat stored therein to the direct heat-transfer area, the area size that contributes to the heat exchange process is not 100 percent of the surface areas of the fins. The fins impact the area size only on the basis of the amounts obtained from the formula "the surface areas of the fins" x "the fin efficiency" including the fin efficiency determined by the shapes of the fins and the circumstances of the surroundings. In contrast, as for the direct heat-transfer areas that are in contact with the mutually-different heat exchanging fluids on the two surfaces thereof, 100 percent of the surface areas thereof are able to contribute to the heat exchange process.
  • the direct heat-transfer area becomes smaller due to the fins being in contact with the direct heat-transfer area, the amount of exchanged latent heat becomes smaller. For this reason, less material is wasted when the direct heat-transfer area is arranged to be as large as possible.
  • a material having moisture permeability is used so that it is possible to exchange the sensible heat as well as the latent heat.
  • ventilation-purpose total heat exchange elements are required to have, at the same time, gas blocking property for preventing the heat exchanging fluids from mixing with each other as well as flame retardant property for ensuring safety.
  • a total heat exchange element is used for ventilating a space such as a living room where living organisms are present, it is required that the amount of released chemicals that may be harmful to human bodies is small, and more specifically, that the amount of released volatile organic compounds (VOCs) is small.
  • the thickness of these members is smaller in terms of permeability of temperature and moisture. It is also preferable when the thickness of these members is smaller, because it is possible to stack more layers in the same height, when the height of the stacked layers of one unit structuring members 20 is smaller; however, if the thickness is too small, problems may arise where, for example, the material strength is not high enough to withstand the processing. Thus, the thickness should be determined by adjusting the processing method being used and other factors. Generally speaking, a material having a thickness in the range approximately from 20 micrometers to 120 micrometers is popularly used.
  • some total heat exchange elements are configured so as to have a multi-layer structure instead of a single-layer structure, so that the abovementioned characteristics are distributed to the different layers (i.e., the first layer has moisture permeability, while the second layer has a certain material strength).
  • the first layer has moisture permeability, while the second layer has a certain material strength.
  • the material for the first wave-form plate members 11, the second wave-form plate members 12, and the flat-plate-like members 13 when a material that has gas blocking property and that contains an alkali metal salt and an alkaline earth metal salt that are water soluble and deliquescent is used, these chemicals store water within the element due to the moisture absorbing action thereof, and at the same time, the chemical liquid diffuses even to the parts where the chemicals were not initially provided because the chemicals dissolve into the stored water. As a result, a problem arises where the amount of chemicals remaining in the partition members, which is needed originally, becomes smaller.
  • the element according to the first embodiment has a structure in which the proportion of the parts other than the partition members is smaller than that in the conventional element, it is possible to ensure a higher level of moisture permeability and a larger amount of exchanged latent heat than the element having the conventional structure and being configured by using the same material.
  • Each of the unit structuring members 20 according to the first embodiment is in the form of a flat plate having a substantially square shape; however, each of the unit structuring members 20 may be in the form of a flat plate having a parallelogram shape or a rectangular shape.
  • the total heat exchange element 101 according to the first embodiment shown in FIG. 1 was manufactured in the following manner: A piece of specially-processed paper was prepared by applying a moisture-permeable-film forming chemical liquid to one of the surfaces of a piece of paper having a thickness of approximately 100 micrometers, the moisture-permeable-film forming chemical liquid being obtained by dissolving polyvinyl alcohol (PVA), which is a watersoluble high-molecular substance, or the like in water and further mixing in lithium chloride serving as a chemical agent that is water soluble and has a moisture absorbing function and guanidine sulfamate serving as a flame retardant.
  • PVA polyvinyl alcohol
  • Another piece of the specially-processed paper prepared in the same manner was processed into a wave-like form with folding creases, was cut into a 120-millimeter square, and was positioned over the abovementioned piece of paper. Subsequently, an aqueous vinyl-acetate resin emulsion adhesive was applied to the apexes of the folding creases of the piece of paper processed into the wave-like form by using a roll coater or the like so as to adhere the pieces of paper together.
  • the height of the wave-like form was arranged so as to be 1.7 millimeters, whereas the distance between any two adjacently-positioned apexes of the wave-like form was arranged so as to be 11.5 millimeters.
  • the spacers 14 were cut out from thick paper having a thickness of approximately 1.2 millimeters so as to fit the shape of the surface of the wave-like form of the second wave-form plate member 12.
  • the spacers 14 were positioned over the second wave-form plate member 12 at the end portions thereof. By applying the aqueous vinyl-acetate resin emulsion adhesive described above with the use of a brush, the spacers 14 were adhered to the two sides of the second wave-form plate member 12 extending parallel to the developing direction of the wave-like form.
  • the spacers 14 After that, after an adhesive is applied to an upper edge of the spacers 14, another piece of the specially-processed paper that is the same as the one used for the second wave-form plate member 12 and that has a thickness of approximately 100 micrometers was pasted onto the spacers so as to fit the wave-like form thereof, as the first wave-form plate member 11.
  • the height (i.e., the width) of the spacers 14 were determined in such a manner that the distance between the first wave-form plate member 11 and the second wave-form plate member 12 in the layer stacking direction was approximately 1.5 millimeters.
  • the unit structuring member 20 was thus produced.
  • a plurality of unit structuring members 20 were prepared in this manner and stacked in the manner of layers while being turned by 90 degrees for each of the layers.
  • the total heat exchange element 101 shown in FIG. 1 was thus obtained.
  • the conventional total heat exchange element 201 shown in FIG. 9 was produced.
  • the wave-like form of the spacers (i.e., the corrugated fins) 211 were shaped so as to be the same as the wave-like forms of the first wave-form plate members 11 and the second wave-form plate members 12 according to the first embodiment.
  • the height of the wave-like form of the spacers 211 was arranged so as to be 1.7 millimeters, whereas the distance between any two adjacently-positioned apexes of the wave-like form was arranged so as to be 11.5 millimeters.
  • the table shown below indicates results of comparing the direct heat-transfer area sizes when an equal number of layers are stacked for Example 1 and for Comparison Example.
  • the direct heat-transfer area size is represented only by the areas of the partition members 213 each of which is in the form of a flat plate.
  • the direct heat-transfer area size is represented by the areas of the flat-plate-like members and the wave-form plate members.
  • the total heat exchange element 101 according to the first embodiment has an extremely larger direct heat-transfer area size per the same volume.
  • the total heat exchange element 101 When the total heat exchange element 101 according to the first embodiment is produced, it should be noted that, even if the total heat exchange element 101 has a structure with a seemingly large direct heat-transfer area size, there is a possibility that the actual heat transfer area size may have become smaller depending on how the fluids flow in the flow passages and there is a possibility that the expected advantageous effect may not be achieved. These possibilities are significantly higher especially when the undulating flow passages are shaped so as to have a rectangular cross section. For example, if the height of the undulating flow passages is configured to be too high, a phenomenon occurs where, as shown in FIG. 3 , the fluid flows only in a straight flow path formed between the upper wave forms and the lower wave forms.
  • FIG. 4 is a drawing of a cross-sectional view of an undulating flow passage having a rectangular cross section in which the apexes formed by the wave-form plate member are sharp.
  • FIG. 5 is a drawing of a cross-sectional view of an undulating flow passage having a rectangular cross section in which each of the apexes formed by the wave-form plate member is shaped with a curvature.
  • FIG. 4 and 5 depict results of simulations performed by allowing a fluid (i.e., air in the present example) to flow in each of these flow passages at mutually the same flow rate.
  • fluid circling regions i.e., dead water regions D2
  • dead water regions D2 occur on the downstream-side wall surfaces of the apexes due to a part of the flow that has been separated.
  • the wall surfaces that are in contact with the dead water regions D2 are seemingly direct heat-transfer areas, these wall surfaces hardly contribute to the heat transfer in actuality.
  • undesirable impacts are made such as a decrease in the heat exchange amount and an increase in the pressure loss.
  • each of the curved portions of the undulating flow passages i.e., the bending parts including the apexes of the wave-form plate members
  • the wave-like form of the wave-form plate members may be in any shape as long as the wave-like form is realized; however, it is desirable if the wave-like form is shaped with a sinusoidal curve or is a triangular wave.
  • the wave-like form may be a rectangular wave; however, when the wave-like form is a rectangular wave, there is a possibility that the level of performance may become lower because the areas in which the flat-plate-like members and the wave-form plate members are in contact with each other are larger.
  • the fluids passing through the undulating flow passages flow so as to collide with a rising portion of the rectangular wave, an increase in the pressure loss is also anticipated.
  • each of the apexes of the wave-like form is shaped with a curvature, it is possible to provide a total heat exchange element having a smaller pressure loss.
  • By reducing the pressure loss it is possible to reduce the input of the fluid power device included in the apparatus into which the total heat exchange element is to be assembled, and also, it is thereby possible to contribute to energy saving of the apparatus.
  • FIG. 6 is a perspective view of a total heat exchange element according to a second embodiment of the present invention.
  • a total heat exchange element 102 according to the second embodiment is configured so that each of the bending parts near the apexes of the first wave-form plate members 11 and the second wave-form plate members 12 is shaped, as shown in FIG. 5 , in a smooth arched form having a predetermined curvature so that no dead water region occurs while the fluids are flowing.
  • a plurality of partition walls 24 are provided between the first wave-form plate members 11 and the second wave-form plate members 12 so as to divide each of the undulating flow passages 31 into a plurality of sections with respect to the width direction thereof and so as to enable the first and the second wave-form plate members 11, 12 to support each other.
  • the other configurations are the same as those.in the first embodiment.
  • the first wave-form plate members 11 and the second wave-form plate members 12 support each other at small intervals.
  • the number of points in which the first and the second wave-form plate members 11, 12 are held is larger, which enhances the structural strengths of the unit structuring members 20 during the manufacturing process and of the entire total heat exchange element 102. It is therefore possible to improve workability and handleability of the element.
  • the configuration contributes to preventing the two fluids used for the heat exchange process from leaking into each other.
  • the element with a large exterior dimension that is partitioned by the plurality of partition walls 24 it is possible to obtain total heat exchange elements each having an arbitrary exterior dimension by cutting the large elements into similarly-shaped elements of arbitrary sizes. As a result, it is possible to change the exterior dimension of the elements without the need to change the mold or the like. This characteristic significantly contributes to improvement of the productivity and enhancement of the degree of freedom in designing the product.
  • FIG. 7 is a perspective view of a total heat exchange element according to a third embodiment of the present invention.
  • a total heat exchange element 103 according to the third embodiment is configured so that partition walls that are provided in the undulating flow passages 31 so as to divide each of the undulating flow passages 31 into a plurality of sections with respect to the width direction thereof are arranged in such a manner that the thickness of the partition wall with respect to the width direction of the flow passage gets larger for one partition wall in every predetermined number of partition walls.
  • partition walls 24b having the smaller thickness and partition walls 24a having the larger thickness are arranged in a predetermined order.
  • the partition walls 24b having the smaller thickness and the partition walls 24a having the larger thickness are provided so as to alternate.
  • Other configurations are the same as those in the second embodiment.
  • the total heat exchange element according to an aspect of the present invention is suitable for an application to a total heat exchange element that performs a heat exchange process on the sensible heat and on the latent heat between two fluids and in which plate members are stacked in the manner of layers.
  • the total heat exchange element according to an aspect of the present invention is optimal for an application to a total heat exchange element to be assembled into a ventilation apparatus or into an air conditioning apparatus so as to perform an air-versus-air total heat exchange process.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (6)

  1. Élément d'échange thermique total (101) dans lequel un premier fluide (A) et un second fluide (B) circulent respectivement à travers un premier passage d'écoulement (31) et un second passage d'écoulement (32) qui sont formés entre des éléments de plaques empilés en couches, de façon à s'étendre dans des directions qui se coupent, de telle sorte qu'une chaleur sensible et qu'une chaleur latente soient échangées entre le premier fluide (A) et le second fluide (B), dans lequel :
    le premier passage d'écoulement (31) est un passage d'écoulement ondulé qui présente une section transversale rectangulaire et est formé en positionnant un premier élément de plaque en forme d'onde (11) qui présente une perméabilité à l'humidité et est formé sous la forme d'une onde ondulant dans une direction d'empilement de couche vers une direction de circulation du fluide, et un second élément de plaque en forme d'onde (12) qui présente une perméabilité à l'humidité et est formé sous la forme d'une onde ondulant sensiblement dans un même cycle que le premier élément de plaque en forme d'onde (11), l'un sur l'autre et avec un intervalle prédéterminé entre eux, et des éléments de fermeture hermétique ferment en outre hermétiquement deux parties latérales par rapport à la direction de circulation du fluide ; et
    le second passage d'écoulement (32) est un passage d'écoulement droit qui présente une section transversale sensiblement triangulaire et est formé entre un élément similaire à une plaque plate (13) présentant une perméabilité à l'humidité et l'un des premier et second éléments de plaque en forme d'onde (11, 12), lorsque l'élément similaire à une plaque plate (13) est positionné sur une surface similaire à une onde de l'un des premier et second éléments de plaque en forme d'onde (11, 12) de façon à être en contact étroit avec celui-ci, caractérisé en ce que :
    l'élément d'échange thermique total (101) comprend en outre une pluralité d'éléments de structure unitaires empilés en couches tout en étant tournés de 90 degrés pour chacune des couches, chacun des éléments de structure unitaires étant configurés avec un ensemble composé du premier élément de plaque en forme d'onde (11), du second élément de plaque en forme d'onde (12), et de l'élément similaire à une plaque plate (13).
  2. Élément d'échange thermique total (101) selon la revendication 1, dans lequel la différence entre la hauteur d'une forme similaire à une onde du premier élément de plaque en forme d'onde (11) et la hauteur d'une forme similaire à une onde du second élément de plaque en forme d'onde (12), est plus grande que la distance, dans la direction d'empilement des couches, entre le premier élément de plaque en forme d'onde (11) et le second élément de plaque en forme d'onde (12).
  3. Élément d'échange thermique total (101) selon la revendication 1, dans lequel chacune des parties courbées au niveau des sommets des formes similaires à une onde du premier élément de plaque en forme d'onde (11) et du second élément de plaque en forme d'onde (12), est mise en forme de façon à présenter une forme arquée ayant une courbure de telle sorte qu'aucune région d'eau morte ne se produise pendant que le premier fluide (A) et le second fluide (B) s'écoulent.
  4. Élément d'échange thermique total (102) selon la revendication 1, dans lequel au moins une cloison de séparation (24) qui divise le passage d'écoulement ondulé présentant la section transversale rectangulaire en une pluralité de sections par rapport à la direction de la largeur de celui-ci, et qui permet aux premier et second éléments de plaque en forme d'onde (11, 12) de se supporter, est prévue entre le premier élément de plaque en forme d'onde (11) et le second élément de plaque en forme d'onde (12).
  5. Élément d'échange thermique total (103) selon la revendication 4, dans lequel :
    une pluralité de cloisons de séparation (24) sont prévues ; et
    les cloisons de séparation (24a) prévues dans une position prédéterminée sont configurées pour présenter une épaisseur plus grande par rapport à la direction de la largeur du passage d'écoulement, que les épaisseurs des autres cloisons de séparation (24b) prévues dans d'autres positions.
  6. Élément d'échange thermique total (101, 102, 103) selon la revendication 1, dans lequel le premier élément de plaque en forme d'onde (11), le second élément de plaque en forme d'onde (12) et l'élément similaire à une plaque plate (13) sont configurés en utilisant un matériau qui présente une propriété de blocage de gaz et qui contient un sel de métal alcalin et un sel de métal alcalino-terreux qui sont solubles dans l'eau et déliquescents.
EP09843988.8A 2009-04-28 2009-04-28 Elément d'échange thermique total Not-in-force EP2426453B1 (fr)

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DE102012008197B4 (de) * 2012-04-26 2018-06-14 Al-Ko Therm Gmbh Austauschsystem zum Austausch von Stoffen zwischen zwei Fluiden
TWI496918B (zh) * 2013-02-05 2015-08-21 Adpv Technology Ltd Intetrust Gas release device for coating process
KR101440723B1 (ko) * 2013-03-14 2014-09-17 정인숙 현열교환기, 이를 포함하는 열회수 환기장치, 및 그 해빙운전과 점검운전 방법
CN104279894A (zh) * 2014-09-23 2015-01-14 大连理工大学 一种堆叠式换热器
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FR3055951B1 (fr) * 2016-09-14 2019-06-14 Commissariat A L'energie Atomique Et Aux Energies Alternatives Echangeur enthalpique a conception simplifiee
JP2018151119A (ja) * 2017-03-13 2018-09-27 サンデンホールディングス株式会社 磁気作業体ユニット及びこれを使用した磁気ヒートポンプ装置
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CN110678698B (zh) * 2017-06-02 2022-02-25 巴斯夫欧洲公司 空调方法和装置
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WO2010125644A1 (fr) 2010-11-04
TW201038902A (en) 2010-11-01
US20120043064A1 (en) 2012-02-23
EP2426453A1 (fr) 2012-03-07
JPWO2010125644A1 (ja) 2012-10-25
EP2426453A4 (fr) 2013-01-09
CN102414534A (zh) 2012-04-11

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