WO2010125644A1 - 全熱交換素子 - Google Patents
全熱交換素子 Download PDFInfo
- Publication number
- WO2010125644A1 WO2010125644A1 PCT/JP2009/058362 JP2009058362W WO2010125644A1 WO 2010125644 A1 WO2010125644 A1 WO 2010125644A1 JP 2009058362 W JP2009058362 W JP 2009058362W WO 2010125644 A1 WO2010125644 A1 WO 2010125644A1
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- WIPO (PCT)
- Prior art keywords
- plate material
- heat exchange
- corrugated plate
- flow path
- total heat
- Prior art date
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Classifications
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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
- 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
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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
- F28D21/0015—Heat and mass exchangers, e.g. with permeable walls
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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
Definitions
- a first fluid and a second fluid such as air are circulated through a first channel and a second channel formed so as to intersect between laminated plate materials, respectively.
- the present invention relates to a total heat exchange element that performs total heat exchange between them.
- a partition member that separates two fluids and a spacing member that retains the spacing between the partition members are provided.
- the partition member has moisture permeability, and heat exchange of sensible heat (temperature) and latent heat (humidity) is simultaneously performed between the two fluids using the partition member as a medium.
- the element since the total heat exchange of the fluid is intended, it is desirable that the element has a large amount of heat exchange.
- the amount of heat exchange is increased by the amount of latent heat exchange heat, and the effect is high.
- cross flow type has a smaller amount of heat exchange per unit volume than the counter flow type.
- counter flow type has a structurally indispensable header (total heat exchange element flow by dividing the two fluids for total heat exchange). This eliminates the need for the portion leading to the path), so that there is an advantage that the actual volume incorporated in the apparatus is small and the processing of the element itself is easy.
- the spacing member is formed in the shape of a corrugated fin.
- the area of the fin in the channel is increased by changing the folding of the fin as in Patent Document 2, for example.
- the channel is narrowed by the volume of the fin itself.
- the pressure loss during fluid passage increases.
- the fins are effective in exchanging sensible heat, but are not effective in exchanging latent heat. Rather, the exchange area of latent heat is reduced by the contact between the fin and the partition member. Therefore, in the case of a total heat exchange element, there is a limit in improving the heat exchange amount by fins in particular.
- Patent Documents 6 to 8 there has been proposed a heat exchange area that is increased by increasing the heat transfer area per unit volume by changing the flow path shape.
- JP-A-4-24492 Japanese Utility Model Publication 1-178471 Japanese Utility Model Publication No. 3-21670 Japanese Patent No. 3805665 JP 2008-232592 A Japanese Utility Model Publication No. 58-165476 Japanese Patent No. 3546574 Japanese Utility Model Publication No. 5-52567
- the pipe diameter is small with respect to the flow rate of the fluid, and the Reynolds number in the pipe is lower than other heat exchangers (approximately 100). It is often in a laminar flow state, and the effect of improving the heat transfer coefficient by changing the fluid flow itself is small in this region. Therefore, fins and protrusions have a greater problem of increased pressure loss than improvement in heat transfer, particularly in the low Reynolds number region. An increase in pressure loss is undesirable because it increases the energy consumed by the power plant for delivering fluid to the total heat exchange element.
- FIG. 8 is a schematic cross-sectional view showing a situation where a dead water area is generated in the flow path.
- a dead water region flow stagnate without flowing along the partition member surface
- D0 may occur in the concave region. Even though it seems that the heat area has been increased, the heat transfer area may actually decrease.
- the present invention has been made in view of the above, and it is possible to increase the heat transfer area per unit volume without using fins, protrusions, or the like, which cause flow inhibition, and without generating a dead water area.
- it is an object to obtain a total heat exchange element in which two intersecting flow paths through which two fluids that exchange heat of sensible heat (temperature) and latent heat (humidity) respectively have the same shape with the same pressure loss. To do.
- it aims at obtaining the total heat exchange element which can change an external dimension easily in addition to this.
- the total heat exchange element of the present invention includes a first flow path and a second flow path that are formed so as to intersect between stacked plate members, respectively.
- a first corrugated plate material that is formed in a wave shape and has moisture permeability, and a second corrugated plate material that is formed in a wave shape having the same amplitude as that of the first corrugated plate material and has moisture permeability are predetermined.
- a flat plate material having moisture permeability is closely adhered to one of the corrugated surfaces of the plate material, and the space between both plate materials Characterized in that it is a direct flow path of the formed substantially triangular cross-section.
- the total heat exchanging element According to the total heat exchanging element according to the present invention, fluids on both sides of almost all surfaces of the plate material being used are circulated, and the flow path shape is also a shape in which a dead water area is unlikely to occur. As a result, the entire heat transfer area is effective, and as a result, the heat transfer area per unit volume increases and the heat exchange amount of the element increases. In addition, when the heat exchange amount may be equal to the conventional one, it is possible to reduce the volume of the element, which can contribute to resource saving. Also, by using moisture-permeable materials for the first corrugated plate material, the second corrugated plate material and the flat plate material, it becomes possible to exchange not only sensible heat but also latent heat, increasing the amount of heat exchange for total heat exchange. There is an effect that can be made.
- FIG. 1 is a perspective view of the total heat exchange element according to the first embodiment of the present invention.
- FIG. 2 is a perspective view for explaining the direction of the fluid flowing through the flow path of the unit constituent member of each stage.
- FIG. 3 is a schematic diagram showing an example in which the dead water area increases when the channel height of the wave channel is too high.
- FIG. 4 is a schematic diagram illustrating an example in which the dead water area increases when the top of the corrugated plate material is bent.
- FIG. 5 is a schematic diagram showing an example in which the dead water area disappears when the top of the corrugated plate is curved with an appropriate curvature.
- FIG. 6 is a perspective view of the total heat exchange element according to the second embodiment of the present invention.
- FIG. 7 is a perspective view of the total heat exchange element according to the third embodiment of the present invention.
- FIG. 8 is a schematic flow diagram when the flow does not follow the corrugated wall surface.
- FIG. 9 is a perspective view of a conventional total heat exchange element used for comparison.
- FIG. 1 is a perspective view of the total heat exchange element according to the first embodiment of the present invention.
- the total heat exchange element 101 of the present embodiment is configured such that a plurality of unit constituent members 20 formed with flow paths are stacked while being rotated by 90 degrees.
- One unit component member 20 includes two corrugated plate members having a moisture permeability (first corrugated plate member 11 and second corrugated plate member 12) and one flat plate member 13 having moisture permeability. It consists of and. In this way, a plurality of unit constituent members 20 made of three plate members are stacked, and one flat plate member 13 is added to the end in the stacking direction to form the total heat exchange element 101.
- the first corrugated plate member 11 and the second corrugated plate member 12 are substantially square and have a wave shape with the same period, and the thickness direction (stacking direction) from one side to the opposite side (toward the Y-axis direction). : Bent in a zigzag cross section in the Z-axis direction) to form a substantially wave shape.
- the first corrugated plate material 11 and the second corrugated plate material 12 formed in this way are arranged apart by a predetermined distance (flow path height) in the stacking direction (Z-axis direction).
- the size of the first corrugated plate material 11 and the second corrugated plate material 12 is processed so that the projected shape on the plane matches the flat plate material 13.
- both ends in the width direction of the flow path are held for the purpose of maintaining the distance between them.
- a spacing member 14 that is bent in a zigzag pattern along the wave shape is sandwiched.
- the spacing member 14 is airtightly fixed to the first corrugated plate member 11 and the second corrugated plate member 12 so that the flowing fluid (air in this example) does not leak.
- the first corrugated plate material 11 and the second corrugated plate material 12 are sealed over the entire length in the flow path direction by the spacing member 14 at both sides of the flow path, and thereby have a rectangular cross section inside.
- the wavy flow path (first flow path) 31 is formed.
- the flat plate member 13 is stacked on the top and bottom of the first corrugated plate member 11 and the second corrugated plate member 12 in the stacking direction (the upper flat plate member 13 is the one additional plate).
- the apexes (ridge lines) of the corrugated plate members 11 and 12 and the flat plate member 13 are fixed in an airtight manner so that the flowing fluid does not leak.
- an orthogonal flow path (second flow path) 32 having a substantially triangular cross section is formed between the first corrugated plate member 11 and the second corrugated plate member 12 and the flat plate member 13.
- the unit component member 20 has a rectangular cross section and an amplitude in the laminating direction with respect to the fluid traveling direction, and a cross section that is orthogonal to the wave flow path 31 and has a substantially triangular cross section.
- a straight flow path 32 is formed that goes straight from the entrance to the exit without meandering.
- a plurality of unit constituent members 20 configured as described above are stacked while being rotated by 90 degrees so that the wave directions intersect each other. In the example of FIG. 1, three unit component members 20 are stacked in the stacking direction (Z-axis direction).
- FIG. 2 is a perspective view for explaining the direction of the fluid flowing through the flow path of the unit constituent member 20 of each stage.
- the first fluid A flowing in the X-axis direction from the right side of FIG. 2 includes the first and third direct flow channels 32 and the second wavy flow channel 31 from the bottom, as indicated by a dashed line arrow in the figure. Circulate.
- the second fluid B that circulates in the Y-axis direction from the left side of FIG. 2 circulates from the bottom to the first and third-stage wave-like channels 31 and the second-stage orthogonal channel 32.
- FIG. 9 is a perspective view showing an example of a conventional total heat exchange element shown for comparison.
- the total heat exchange element 201 in FIG. 9 is configured by alternately laminating flat partition members 213 and spacing members (corrugated fins) 211 whose cross-sections are shaped into corrugated fins.
- the uniting member 220 is manufactured by laminating one partition member 213 and one spacing member 211 so that the wave-shaped convex portions are in contact with each other and fixing them by bonding or the like. Then, the unit constituent members 220 are laminated so that the partition members 213 and the spacing members 211 are alternately arranged, and the opening directions of the wave-shaped openings of the spacing members 211 are alternately about 90 degrees. (In the example of FIG.
- the first corrugated plate material 11 and the second corrugated plate material 12 of the present embodiment serve as a medium during heat exchange, and correspond to the partition member 213 of the conventional example in FIG.
- the greatest feature of the total heat exchange element of this embodiment is that almost all wall surfaces other than the spacing member in the element are not indirectly heat transfer surfaces such as fins, and different heat exchange fluids are allowed to flow on both surfaces. Since the structure is a direct heat transfer surface, the material is not wasted and the heat transfer area per unit volume of the element can be increased. Since fins transfer heat by directly applying the heat stored in them to the heat transfer surface, the area that contributes to heat exchange is not 100% of the surface area of the fins, but the fin efficiency determined by the shape of the fins and the surrounding conditions is used. And It can only be affected by the amount given by fin surface area x fin efficiency. However, the direct heat transfer surface that comes into contact with different heat exchange fluids on both sides can contribute to 100% heat exchange.
- the first corrugated plate member 11, the second corrugated plate member 12, and the flat plate member 13 of the present embodiment are those having moisture permeability in order to exchange sensible heat and latent heat. Further, in the total heat exchange element for ventilation, gas shielding properties for preventing the heat exchange fluids from mixing with each other and flame resistance for ensuring safety are also required. Furthermore, when it is used for ventilation of living spaces such as living rooms, it emits less harmful chemical substances, more specifically volatile organic compounds (VOCs) to humans, and unpleasant odors. There is a need for material strength that can withstand pressure during device processing and use. Therefore, the corrugated plate material 11, the second corrugated plate material 12, and the flat plate material 13 are made of materials satisfying the above.
- the thickness of these plate materials is thin because it is advantageous in terms of transmission of temperature and humidity, and the stacking height of one layer of the unit constituent member 20 is reduced, so that more layers can be stacked at the same height.
- the material strength cannot withstand the processing, and it is determined by adjustment with the processing method and others.
- about 20 to 120 ⁇ m is often used.
- the total heat exchange element has a multilayer structure instead of a single layer so that the above properties are dispersed (for example, moisture permeability in the first layer, material strength in the second layer, etc.
- an alkali metal salt and an alkaline earth metal salt which have gas shielding properties, water solubility and deliquescence are included.
- these chemicals are originally necessary because they store water in the element due to the self-moisture absorption function, and at the same time, the chemical solution diffuses to the part where the chemical was not originally added by dissolving in the water.
- the amount of drug remaining on the partition member is reduced, but the ratio of the part other than the partition member is reduced in the structure of this element compared to the conventional element. Therefore, higher moisture permeability and latent heat exchange amount can be ensured.
- unit component member 20 of the present embodiment has a substantially square flat plate shape, it may have a parallelogram or rectangular flat plate shape.
- the total heat exchange element 101 of the present embodiment shown in FIG. 1 was produced as follows. Polyethylene alcohol (PVA), which is a water-soluble polymer substance, is dissolved in water in a paper with a thickness of about 100 ⁇ m. A water-based vinyl acetate resin emulsion adhesive layered with a specially processed paper coated with a chemical solution for forming a wet film, and a specially processed paper that has been processed into a wavy shape with a crease cut into a 120mm square. Is applied to the top of the crease of the wavy processed paper using a roll coater.
- PVA Polyethylene alcohol
- a water-based vinyl acetate resin emulsion adhesive layered with a specially processed paper coated with a chemical solution for forming a wet film, and a specially processed paper that has been processed into a wavy shape with a crease cut into a 120mm square. Is applied to the top of the crease of the wavy processed paper using a roll coater.
- a jig or the like was devised so that the height of the wave was 1.7 mm and the length from the top to the top of the wave was 11.5 mm.
- a spacing member 14 cut out from a thick paper sheet having a thickness of about 1.2 mm in accordance with the wavy surface shape of the second wavy plate member 12 is stacked on the end portion of the second wavy plate member 12, and then brushed.
- the same water-based vinyl acetate resin emulsion adhesive was applied to adhere the two corrugated plate members 12 to both two sides parallel to the traveling direction of the corrugated shape.
- the height (width) of the spacing member 14 was determined so that the distance in the stacking direction of the first corrugated plate material 11 and the second corrugated plate material 12 was about 1.5 mm.
- a plurality of unit constituent members 20 produced in this way were prepared and stacked while rotating each by 90 degrees to obtain the total heat exchange element 101 of FIG.
- a conventional total heat exchange element 201 shown in FIG. 9 was produced for comparison with the total heat exchange element 101 of the present embodiment.
- the corrugated shape of the spacing member (corrugated fin) 211 was made the same as the corrugated shape of the first corrugated plate member 11 and the second corrugated plate member 12 of the above embodiment. That is, the height of the wave of the spacing member 211 is 1.7 mm, and the length from the top to the top of the wave is 11.5 mm.
- Example 1 Comparative Example
- the following table compares the size of the direct heat transfer area when the same number of layers as in Example 1 and Comparative Example are stacked.
- the direct heat transfer area is only the area of the flat partition member 213, whereas the shape of Example 1 is the direct heat transfer area of the flat plate material and the corrugated plate material.
- the direct heat transfer area per volume is very large.
- the actual heat transfer area is reduced depending on how the fluid flows in the flow path, even if the structure has an apparent direct heat transfer area. It is possible that the expected effect may not be obtained. This is particularly noticeable in the shape of a wave-like channel having a rectangular cross section. For example, when the channel height of the wave-like channel is increased, if it is too high, as shown in FIG. A phenomenon occurs in which the fluid flows only into the generated straight flow path. In such a case, since the dead water region D1 of the circulating flow that is actually generated between the wall surface and the fluid to be heat-exchanged (mostly flows in the straight flow path) is insulated, the effect as the heat transfer area is achieved. Disappear.
- the distance between the corrugated channels is made smaller than the wave height of the corrugated plate material, the top of the corrugated plate material on the upper surface and the top of the corrugated plate material on the lower surface will be mated with each other, so a straight flow channel will not be generated. As a result, it is desirable because it can suppress the occurrence of dead water areas.
- FIG. 4 is a cross-section of a rectangular cross-sectional wavy flow path with a sharp top of the corrugated plate material
- FIG. 5 is a cross-section of the rectangular cross-sectional wavy flow path when the top of the corrugated plate material is curved.
- This is a simulation of the flow of fluid (in this case, air) when the same flow rate is applied.
- region namely, dead water area D2 of the fluid formed by the flow separating on the downstream side wall surface of the top part is generated.
- the wall surface in contact with the dead water area D2 is a direct heat transfer surface, it actually contributes little to heat transfer. In this way, when the dead water area D2 is generated, it results in undesirable effects such as a decrease in heat exchange amount and an increase in pressure loss.
- the bent portion of the corrugated flow path that is, the shape of the folded portion including the top of the corrugated plate material is not used as the shape in which the plane is bent as in the first embodiment.
- the waveform of the corrugated plate may be any shape as long as it is a waveform, but a sine curve or a triangular wave is desirable.
- a rectangular wave may be used, but in the case of a rectangular wave, the contact area between the flat plate material and the corrugated plate material may be widened and the performance may be deteriorated, and the fluid passing through the corrugated flow path is rectangular. Since it flows in the form of colliding with the rising part of the wave, there is a concern that the pressure loss increases.
- a total heat exchange element with a lower pressure loss can be provided.
- By reducing the pressure loss it is possible to reduce the input of the fluid power unit of the equipment to be incorporated, contributing to the reduction of the energy of the equipment.
- FIG. FIG. 6 is a perspective view of the total heat exchange element according to the second embodiment of the present invention.
- the shape of the folded portion in the vicinity of the wave-shaped top portions of the first corrugated plate material 11 and the second corrugated plate material 12 is such that a fluid flows as shown in FIG. When it does, it becomes the smooth curve shape of the predetermined curvature in which a dead water area is not formed.
- the corrugated flow path 31 is divided into a plurality in the flow path width direction between the first corrugated plate material 11 and the second corrugated plate material 12, and both plate materials are used.
- a plurality of partition walls 24 that support 11 and 12 are provided. Other configurations are the same as those in the first embodiment.
- the first corrugated plate member 11 and the second corrugated plate member 12 are mutually supported at a narrow interval, so that the two plate members 11 and 12 are held.
- the number of points increases, and the structural strength of the unit component member 20 and the entire heat exchange element 102 in the middle of manufacture increases, and the workability and handling of the element can be improved. Moreover, it contributes to prevention of leakage between two fluids that exchange heat.
- the element is designed in advance as an element having a large outer dimension by partitioning with a plurality of partition walls 24, it can be cut into a similar shape of an arbitrary size, A total heat exchange element of dimensions can be obtained. Therefore, the external dimensions can be changed without changing the mold or the like. This greatly contributes to the improvement of production efficiency and the freedom of product design.
- FIG. 7 is a perspective view of the total heat exchange element according to the third embodiment of the present invention.
- the partition wall provided in the wave-like channel 31 and dividing the wave-like channel 31 into a plurality of channels in the channel width direction has a thickness in the channel width direction of the partition wall. Is increased for every predetermined number of sheets. That is, the partition wall 24b having a small thickness and the partition wall 24a having a large thickness are provided side by side in a predetermined order. In the present embodiment, the partition wall 24b having a small thickness and the partition wall 24a having a large thickness are alternately provided. Other configurations are the same as those of the second embodiment.
- an element having an arbitrary external dimension can be obtained by cutting with an arbitrary dimension, but the end of the obtained element depends on the relationship between the position of the partition wall and the cutting position, but is largely wasted. There is a possibility that part will be made.
- the width dimension is not determined unless the cutting position of the element is determined, it becomes difficult to design and prepare the structure. Therefore, although there is a restriction on the cutting position, if the center of the thick part of the partition wall is cut, it is possible to obtain a similar element in which the end part has no useless part.
- the total heat exchange element according to the present invention is suitable for being applied to a plate-type laminated total heat exchange element that exchanges sensible heat and latent heat between two fluids. It is optimally applied to a total heat exchange element which is incorporated in an air conditioner and is suitable for performing a total heat exchange between air and air.
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Abstract
Description
12 第2の波状板材
13 平板状板材
14 間隔保持部材
20 単位構成部材
24,24a、24b 仕切壁
31 波状流路(第1の流路)
32 直行流路(第2の流路)
101,102,103 全熱交換素子
A 第1の流体
B 第2の流体
D0,D1,D2 死水域
図1は、本発明にかかる実施の形態1の全熱交換素子の斜視図である。説明が明確となるように図中に記載の座標軸を使って方向を補助的に説明するがこれに限定されるものではない。本実施の形態の全熱交換素子101は、流路が形成された複数個の単位構成部材20が90度ずつ回転させながら複数個積層されて構成されている。1個の単位構成部材20は、波状に形成された透湿性を有する2枚の波状板材(第1の波状板材11及び第2の波状板材12)と透湿性を有する1枚の平板状板材13とから構成されている。このように3枚の板材で成る単位構成部材20が複数個積層されて更に1枚の平板状板材13が積層方向端部に追加されて全熱交換素子101が出来ている。
フィン表面積×フィン効率
で与えられる量でしか影響できない。しかし両面で異なる被熱交換流体と接触する直接伝熱面は、その表面積が100%熱交換に寄与することができる。
次のようにして、図1に示す本実施の形態の全熱交換素子101を作製した。
厚さ100μm程度の紙に水溶性高分子物質であるポリビニルアルコール(PVA)等を水に溶かし、さらに水溶性で吸湿作用のある薬剤としての塩化リチウムと、難燃剤としてスルファミン酸グアニジンを混合した透湿膜形成用の薬液を片面塗布した特殊加工紙と、同じく加工した特殊加工紙を折り目をつけて波状に加工したものを一片120mmの方形に切断したものを重ね、水系酢酸ビニル樹脂エマルジョン接着剤を波状加工した紙の折り目の頂部にロールコーター等を使って塗布し接着する。
一方、本実施の形態の全熱交換素子101との比較のために、図9に示す従来の全熱交換素子201を作製した。このとき、間隔保持部材(コルゲートフィン)211の波形形状を、上記実施例の第1の波状板材11及び第2の波状板材12の波形形状と同じにした。つまり、間隔保持部材211の波の高さを1.7mm、波の頂部から頂部までの長さを11.5mmとした。
上記実施例1、比較例をそれぞれ同じ層数だけ積層した時の直接伝熱面積の大きさを比較したものが以下の表である。従来例では直接伝熱面積が平板状の仕切部材213の面積のみであるのに対し、実施例1の形状は平板状板材及び波状板材の面積が直接伝熱面積となるため、本実施の形態の全熱交換素子101の場合、同じ体積あたりの直接伝熱面積が非常に大きくなる。
図6は、本発明にかかる実施の形態2の全熱交換素子の斜視図である。本実施の形態の全熱交換素子102においては、第1の波状板材11及び第2の波状板材12の波形状の頂部近傍の折り返し部の形状は、図5に示したような、流体が流通したとき、死水域が形成されない所定の曲率の滑らかな湾曲形状となっている。また、本実施の形態の全熱交換素子102においては、第1の波状板材11と第2の波状板材12との間に、波状流路31を流路幅方向に複数に分割するとともに両板材11,12を相互に支持する複数の仕切壁24が設けられている。その他の構成は実施の形態1と同様である。
図7は、本発明にかかる実施の形態3の全熱交換素子の斜視図である。本実施の形態の全熱交換素子103においては、波状流路31内に設けられて当該波状流路31を流路幅方向に複数に分割する仕切壁において、仕切壁の流路幅方向厚さが、所定枚数毎に大きくされている。すなわち、厚さの小さい仕切壁24bと厚さの大きい仕切壁24aとが所定の順番にて併設されている。本実施の形態では、厚さの小さい仕切壁24bと厚さの大きい仕切壁24aとが交互に設けられている。その他の構成は実施の形態2と同様である。
Claims (7)
- 積層された板材間に交差するように形成された第1の流路と第2の流路に、それぞれ第1の流体と第2の流体を流通させ、両流体間で顕熱及び潜熱を交換させる全熱交換素子であって、
前記第1の流路は、流体の進行方向に向かって積層方向に振幅するように波状に形成されて透湿性を有する第1の波状板材と、該第1の波状板材と概略同じ周期で振幅する波状に形成されて透湿性を有する第2の波状板材とが所定の間隔を空けて重ねられて、流体の進行方向両側部が密閉部材により密閉されて形成された矩形断面の波状流路であり、
前記第2の流路は、前記第1の波状板材と前記第2の波状板材のいずれか一方の波状面に透湿性を有する平板状板材が密着して重ねられて両板材間に形成された概略三角形断面の直行流路である
ことを特徴とする全熱交換素子。 - 1組の前記第1の波状板材、前記第2の波状板材、及び前記平板状板材で成る単位構成部材が、90度ずつ回転させながら複数積層されている
ことを特徴とする請求項1に記載の全熱交換素子。 - 前記第1の波状板材及び前記第2の波状板材の波形状の高低差は、前記第1の波状板材及び前記第2の波状板材の積層方向距離よりも大きい
ことを特徴とする請求項1に記載の全熱交換素子。 - 前記第1の波状板材及び前記第2の波状板材の波形状の頂点折り返し部の形状は、前記第1の流体及び前記第2の流体が流通したとき、死水域が形成されない曲率の湾曲形状となっている
ことを特徴とする請求項1に記載の全熱交換素子。 - 前記第1の波状板材及び前記第2の波状板材の間に、前記矩形断面の波状流路を流路幅方向に複数に分割するとともに、前記第1の波状板材と前記第2の波状板材との間で、相互に支持する少なくとも1つの仕切壁が設けられている
ことを特徴とする請求項1に記載の全熱交換素子。 - 前記仕切壁は、複数個が設けられており、所定の位置の前記仕切壁は、他の位置の前記仕切壁よりも流路幅方向厚さが大きくされている
ことを特徴とする請求項5に記載の全熱交換素子。 - 前記第1の波状板材、前記第2の波状板材、及び前記平板状板材は、気体遮蔽性を有し、さらに水溶性でかつ潮解性を有するアルカリ金属塩およびアルカリ土類金属塩を含んだものを用いる
ことを特徴とする請求項1に記載の全熱交換素子。
Priority Applications (6)
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US13/264,906 US20120043064A1 (en) | 2009-04-28 | 2009-04-28 | Total heat exchange element |
PCT/JP2009/058362 WO2010125644A1 (ja) | 2009-04-28 | 2009-04-28 | 全熱交換素子 |
EP09843988.8A EP2426453B1 (en) | 2009-04-28 | 2009-04-28 | Total heat exchange element |
JP2011511213A JPWO2010125644A1 (ja) | 2009-04-28 | 2009-04-28 | 全熱交換素子 |
CN2009801589881A CN102414534A (zh) | 2009-04-28 | 2009-04-28 | 全热交换元件 |
TW098118888A TW201038902A (en) | 2009-04-28 | 2009-06-06 | Total heat exchange element |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013145068A (ja) * | 2012-01-13 | 2013-07-25 | Panasonic Corp | 熱交換素子とそれを用いた熱交換型換気機器 |
WO2019026102A1 (ja) * | 2017-07-31 | 2019-02-07 | 三菱電機株式会社 | 全熱交換素子および熱交換換気装置 |
WO2024058113A1 (ja) * | 2022-09-12 | 2024-03-21 | パナソニックIpマネジメント株式会社 | 投写型画像表示装置 |
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---|---|---|---|---|
DE102012008197B4 (de) * | 2012-04-26 | 2018-06-14 | Al-Ko Therm Gmbh | Austauschsystem zum Austausch von Stoffen zwischen zwei Fluiden |
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Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58165476U (ja) | 1982-04-26 | 1983-11-04 | 株式会社東芝 | 熱交換器 |
JPS6329195A (ja) * | 1986-07-18 | 1988-02-06 | Matsushita Seiko Co Ltd | ハニカム型熱交換器 |
JPH01178471U (ja) | 1988-05-27 | 1989-12-20 | ||
JPH02238293A (ja) * | 1989-03-10 | 1990-09-20 | Daikin Ind Ltd | 熱交換装置 |
JPH0321670U (ja) | 1989-05-15 | 1991-03-05 | ||
JPH0424492A (ja) | 1990-05-21 | 1992-01-28 | Matsushita Electric Ind Co Ltd | 熱交換素子 |
JPH0552567U (ja) | 1991-12-05 | 1993-07-13 | 株式会社荏原製作所 | 熱交換素子 |
JPH06313693A (ja) * | 1993-04-28 | 1994-11-08 | K G Pack Kk | 熱交換機エレメント用材料および熱交換機エレメント |
JP2000097590A (ja) * | 1998-09-24 | 2000-04-04 | Hisaka Works Ltd | プレート式熱交換器 |
JP2001215093A (ja) * | 2000-02-02 | 2001-08-10 | Matsushita Electric Ind Co Ltd | 積層式熱交換器およびその製造方法 |
JP3546574B2 (ja) | 1996-01-08 | 2004-07-28 | 三菱電機株式会社 | 熱交換器 |
JP2005516171A (ja) * | 2001-06-06 | 2005-06-02 | バッテル・メモリアル・インスティチュート | 流体処理装置及びその方法 |
JP2006064342A (ja) * | 2004-08-30 | 2006-03-09 | Nitta Ind Corp | 熱交換素子 |
JP3805665B2 (ja) | 2001-11-06 | 2006-08-02 | 株式会社豊田中央研究所 | 熱交換器 |
JP2007315649A (ja) * | 2006-05-24 | 2007-12-06 | Mitsubishi Electric Corp | 全熱交換器 |
JP2008232592A (ja) | 2007-03-23 | 2008-10-02 | Univ Of Tokyo | 熱交換器 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02217789A (ja) * | 1989-02-15 | 1990-08-30 | Daikin Ind Ltd | 熱交換エレメント及び熱交換装置 |
-
2009
- 2009-04-28 EP EP09843988.8A patent/EP2426453B1/en not_active Not-in-force
- 2009-04-28 JP JP2011511213A patent/JPWO2010125644A1/ja active Pending
- 2009-04-28 US US13/264,906 patent/US20120043064A1/en not_active Abandoned
- 2009-04-28 WO PCT/JP2009/058362 patent/WO2010125644A1/ja active Application Filing
- 2009-04-28 CN CN2009801589881A patent/CN102414534A/zh active Pending
- 2009-06-06 TW TW098118888A patent/TW201038902A/zh unknown
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58165476U (ja) | 1982-04-26 | 1983-11-04 | 株式会社東芝 | 熱交換器 |
JPS6329195A (ja) * | 1986-07-18 | 1988-02-06 | Matsushita Seiko Co Ltd | ハニカム型熱交換器 |
JPH01178471U (ja) | 1988-05-27 | 1989-12-20 | ||
JPH02238293A (ja) * | 1989-03-10 | 1990-09-20 | Daikin Ind Ltd | 熱交換装置 |
JPH0321670U (ja) | 1989-05-15 | 1991-03-05 | ||
JPH0424492A (ja) | 1990-05-21 | 1992-01-28 | Matsushita Electric Ind Co Ltd | 熱交換素子 |
JPH0552567U (ja) | 1991-12-05 | 1993-07-13 | 株式会社荏原製作所 | 熱交換素子 |
JPH06313693A (ja) * | 1993-04-28 | 1994-11-08 | K G Pack Kk | 熱交換機エレメント用材料および熱交換機エレメント |
JP3546574B2 (ja) | 1996-01-08 | 2004-07-28 | 三菱電機株式会社 | 熱交換器 |
JP2000097590A (ja) * | 1998-09-24 | 2000-04-04 | Hisaka Works Ltd | プレート式熱交換器 |
JP2001215093A (ja) * | 2000-02-02 | 2001-08-10 | Matsushita Electric Ind Co Ltd | 積層式熱交換器およびその製造方法 |
JP2005516171A (ja) * | 2001-06-06 | 2005-06-02 | バッテル・メモリアル・インスティチュート | 流体処理装置及びその方法 |
JP3805665B2 (ja) | 2001-11-06 | 2006-08-02 | 株式会社豊田中央研究所 | 熱交換器 |
JP2006064342A (ja) * | 2004-08-30 | 2006-03-09 | Nitta Ind Corp | 熱交換素子 |
JP2007315649A (ja) * | 2006-05-24 | 2007-12-06 | Mitsubishi Electric Corp | 全熱交換器 |
JP2008232592A (ja) | 2007-03-23 | 2008-10-02 | Univ Of Tokyo | 熱交換器 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2426453A4 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013145068A (ja) * | 2012-01-13 | 2013-07-25 | Panasonic Corp | 熱交換素子とそれを用いた熱交換型換気機器 |
WO2019026102A1 (ja) * | 2017-07-31 | 2019-02-07 | 三菱電機株式会社 | 全熱交換素子および熱交換換気装置 |
WO2024058113A1 (ja) * | 2022-09-12 | 2024-03-21 | パナソニックIpマネジメント株式会社 | 投写型画像表示装置 |
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EP2426453A1 (en) | 2012-03-07 |
TW201038902A (en) | 2010-11-01 |
EP2426453A4 (en) | 2013-01-09 |
EP2426453B1 (en) | 2013-10-02 |
US20120043064A1 (en) | 2012-02-23 |
JPWO2010125644A1 (ja) | 2012-10-25 |
CN102414534A (zh) | 2012-04-11 |
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