WO2010125643A1 - Heat exchange element - Google Patents
Heat exchange element Download PDFInfo
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- WO2010125643A1 WO2010125643A1 PCT/JP2009/058361 JP2009058361W WO2010125643A1 WO 2010125643 A1 WO2010125643 A1 WO 2010125643A1 JP 2009058361 W JP2009058361 W JP 2009058361W WO 2010125643 A1 WO2010125643 A1 WO 2010125643A1
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- plate material
- heat exchange
- corrugated
- corrugated plate
- flow path
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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
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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
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 heat exchange element that performs 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. It is common.
- heat is exchanged between two fluids using a partition member as a medium.
- a heat exchange element is desired to have a large amount of heat exchange for the purpose of heat exchange of fluid.
- cross flow type There are two types of heat exchange elements: cross flow type and counter flow type.
- the cross-flow type has a smaller amount of heat exchange per unit volume than the counter-flow type.
- the cross-flow type header which is structurally indispensable (divides the two fluids to be exchanged into the heat exchange element flow path Therefore, there is an advantage that the actual volume incorporated in the apparatus is small and the device itself can be easily processed.
- 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. Therefore, there is a limit to the improvement of the heat exchange fee by such fins.
- 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 to In many cases, it becomes a laminar flow state, and in this region, the effect of improving the heat transfer coefficient by changing the fluid flow itself is small. 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 sending fluid to the 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. Further, it is an object to obtain a heat exchange element having the same shape in which the two-way flow paths through which the heat exchange fluid flows have the same pressure loss. Furthermore, it aims at obtaining the heat exchange element which can change an external dimension easily in addition to this.
- the heat exchange element of the present invention includes a first flow path and a second flow path formed so as to intersect each other between the stacked plate members.
- the heat exchange element that circulates the first fluid and the second fluid and exchanges heat between the two fluids, the first flow path is formed in a wave shape so as to swing in the laminating direction toward the fluid traveling direction.
- the first corrugated plate material and the second corrugated plate material having an amplitude substantially the same as that of the first corrugated plate material are overlapped at a predetermined interval, and both sides in the fluid traveling direction are sealed by the spacing member.
- the second channel has a rectangular cross-sectional wavy flow path, and a flat plate is closely attached to one of the first wavy plate and the second wavy plate. It is an orthogonal flow path having a substantially triangular cross section formed between plate materials.
- the heat exchanging element According to the heat exchanging element according to the present invention, fluids on both sides of almost all surfaces of the plate material used are circulated, and the flow path shape is also a shape in which a dead water area is unlikely to occur. Almost all become effective heat transfer areas. As a result, the heat transfer area per unit volume increases, and the heat exchange amount of the element increases. Further, when the heat exchange amount may be equal to the conventional amount, it is possible to reduce the volume of the element, which can contribute to resource saving.
- FIG. 1 is a perspective view of the 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 heat exchange element according to the second embodiment of the present invention.
- FIG. 7 is a perspective view of the 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 heat exchange element used for comparison
- FIG. 1 is a perspective view of the heat exchange element according to the first embodiment of the present invention.
- the 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 (first corrugated plate member 11 and second corrugated plate member 12) formed in a corrugated shape and one flat plate member 13. In this way, a plurality of unit component 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 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 first fluid A and the second fluid B exchange heat using the first corrugated plate material 11, the second corrugated plate material 12, and the flat plate material 13 as a medium during heat exchange.
- the two-way flow paths through which the heat exchange fluid flows are formed in two types, the wave-shaped flow path 31 and the direct flow path 32, and have the same shape. it can.
- FIG. 9 is a perspective view showing an example of a conventional heat exchange element shown for comparison.
- the heat exchange element 201 of FIG. 9 is configured by alternately laminating flat partition members 213 and interval holding 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 heat exchange element of the present embodiment is that almost all wall surfaces other than the spacing member in the element are not indirectly heat transfer surfaces such as fins, but 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. Therefore, it can be said that there is no waste in the material when the direct heat transfer surface is increased as much as possible.
- 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 heat exchange element 101 of the present embodiment shown in FIG. 1 was produced as follows.
- the second corrugated plate material 12 is creased as a second corrugated plate material 12 to a specially processed paper having a thickness of about 100 ⁇ m to be the flat plate material 13 (processing to close the eyes of the paper with resin etc. so that air does not leak).
- a sheet of specially processed paper with a thickness of about 100 ⁇ m, cut to 120 mm on each side, is layered, and a water-based vinyl acetate resin emulsion adhesive is applied to the top of the wavy processed paper fold using a roll coater or the like and bonded. .
- 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 laminated while rotating each by 90 degrees to obtain the heat exchange element 101 of FIG.
- a conventional heat exchange element 201 shown in FIG. 9 was produced for comparison with the 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 the same volume becomes very large.
- the actual heat transfer area decreases depending on the flow of fluid in the flow path, even if the structure has a large direct heat transfer area. There is a possibility 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 occur. 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 peeling on the downstream side wall surface of the top part has generate
- 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. 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 heat exchange element with 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 heat exchange element according to the second embodiment of the present invention.
- the shape of the folded portion in the vicinity of the top of the corrugated portions of the first corrugated plate material 11 and the second corrugated plate material 12 circulates as shown in FIG.
- the dead water area When the dead water area is not formed, it has a smooth curved shape with a predetermined curvature.
- the corrugated channel 31 is divided into a plurality in the channel width direction between the first corrugated plate member 11 and the second corrugated plate member 12, and both the plate members 11. , 12 are provided with a plurality of partition walls 24 that support each other.
- Other configurations are the same as those of 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 constituent member 20 and the heat exchange element 102 in the middle of manufacture increases, and the workability and handleability 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 heat exchange element with 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. FIG. 7 is a perspective view of the heat exchange element according to the third embodiment of the present invention.
- the partition wall provided in the corrugated channel 31 and dividing the corrugated channel 31 into a plurality of channels in the channel width direction has a thickness in the channel width direction of the partition wall.
- the size is increased every predetermined number. 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 heat exchange element according to the present invention is suitable for being applied to a cross-flow cross-flow heat exchange element of a plate material type that performs heat exchange between two fluids having different temperatures. It is optimally applied to a cross flow heat exchange element that is incorporated in a conditioner and is suitable for air-to-air heat exchange.
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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 熱交換素子
A 第1の流体
B 第2の流体
D0,D1,D2 死水域 DESCRIPTION OF
32 Direct flow path (second flow path)
101, 102, 103 Heat exchange element A 1st fluid B 2nd fluid D0, D1, D2 Dead water area
図1は、本発明にかかる実施の形態1の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熱交換素子101が出来ている。 Embodiment 1 FIG.
FIG. 1 is a perspective view of the heat exchange element according to the first embodiment of the present invention. In order to clarify the explanation, the direction is supplementarily explained using the coordinate axes shown in the figure, but the present invention is not limited to this. The
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。したがって極力直接伝熱面を多くしたほうが材料に無駄が無いと言える。 The greatest feature of the heat exchange element of the present embodiment is that almost all wall surfaces other than the spacing member in the element are not indirectly heat transfer surfaces such as fins, but 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. Therefore, it can be said that there is no waste in the material when the direct heat transfer surface is increased as much as possible.
次のようにして、図1に示す本実施の形態の熱交換素子101を作製した。
平板状板材13となる厚さ100μm程度の特殊加工紙(空気が漏洩しないように樹脂などで紙の目を塞ぐ加工などを施した)に、第2の波状板材12として、折り目をつけて波状に加工した同じく厚さ100μm程度の特殊加工紙を一辺120mm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した。 <Example 1>
The
The second
一方、本実施の形態の熱交換素子101との比較のために、図9に示す従来の熱交換素子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。 <Comparative example>
On the other hand, a conventional
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。 <Comparison>
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. In the conventional example, the direct heat transfer area is only the area of the
図6は、本発明にかかる実施の形態2の熱交換素子の斜視図である。本実施の形態の熱交換素子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。
FIG. 6 is a perspective view of the heat exchange element according to the second embodiment of the present invention. In the
図7は、本発明にかかる実施の形態3の熱交換素子の斜視図である。本実施の形態の熱交換素子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。 Embodiment 3 FIG.
FIG. 7 is a perspective view of the heat exchange element according to the third embodiment of the present invention. In the
Claims (6)
- 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、両流体間で熱交換を行なう熱交換素子において、
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た第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た第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間隔保持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形状に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熱交換素子。 Heat exchange in which the first fluid and the second fluid are circulated through the first channel and the second channel formed so as to intersect between the stacked plate members, and heat exchange is performed between the two fluids. In the element
The first flow path is formed in a corrugated first corrugated plate material having an amplitude in the laminating direction toward the fluid traveling direction, and in a corrugated shape having substantially the same period as that of the first corrugated plate material. The second corrugated plate material is overlapped with a predetermined interval, and both sides of the fluid in the traveling direction are hermetically sealed with a spacing member, and a rectangular cross-sectional corrugated flow path,
The second flow path has a substantially triangular cross-section formed between the two plate members by laminating a flat plate member in close contact with one of the first wavy plate member and the second wavy plate member. A heat exchange element characterized by being a direct flow path. - 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に記載の熱交換素子。 2. A plurality of unit constituent members made of one set of the first corrugated plate material, the second corrugated plate material, and the flat plate material are laminated while being rotated by 90 degrees. Heat exchange element. - 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に記載の熱交換素子。 The height difference of the corrugated shape of the first corrugated plate material and the second corrugated plate material is larger than the stacking direction distance between the first corrugated plate material and the second corrugated plate material. The heat exchange element as described. - 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に記載の熱交換素子。 The shape of the wave-like vertex folding portion of the first corrugated plate material and the second corrugated plate material is a curved shape with a curvature that does not form a dead water area when the first fluid and the second fluid flow. The heat exchange element according to claim 1, wherein: - 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に記載の熱交換素子。 Between the first corrugated plate material and the second corrugated plate material, the corrugated flow path having the rectangular cross section is divided into a plurality of channels in the flow path width direction, and the first corrugated plate material and the second corrugated plate material The heat exchange element according to claim 1, wherein at least one partition wall that supports each other is provided. - 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に記載の熱交換素子。 A plurality of the partition walls are provided, and the partition wall at a predetermined position has a thickness in the flow path width direction larger than that of the partition walls at other positions. The heat exchange element according to 1.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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JP2011511212A JPWO2010125643A1 (en) | 2009-04-28 | 2009-04-28 | Heat exchange element |
US13/265,003 US20120037349A1 (en) | 2009-04-28 | 2009-04-28 | Heat exchange element |
PCT/JP2009/058361 WO2010125643A1 (en) | 2009-04-28 | 2009-04-28 | Heat exchange element |
CN2009801589877A CN102414533A (en) | 2009-04-28 | 2009-04-28 | Heat exchange element |
TW098119195A TWI421460B (en) | 2009-04-28 | 2009-06-09 | Heat exchange element |
Applications Claiming Priority (1)
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PCT/JP2009/058361 WO2010125643A1 (en) | 2009-04-28 | 2009-04-28 | Heat exchange element |
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WO2010125643A1 true WO2010125643A1 (en) | 2010-11-04 |
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PCT/JP2009/058361 WO2010125643A1 (en) | 2009-04-28 | 2009-04-28 | Heat exchange element |
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US (1) | US20120037349A1 (en) |
JP (1) | JPWO2010125643A1 (en) |
CN (1) | CN102414533A (en) |
TW (1) | TWI421460B (en) |
WO (1) | WO2010125643A1 (en) |
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US10727552B2 (en) * | 2015-11-04 | 2020-07-28 | Ford Global Technologies, Llc | Heat exchanger plate for electrified vehicle battery packs |
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EP4343259A3 (en) * | 2020-08-21 | 2024-06-19 | Mitsubishi Electric Corporation | Heat exchange element and heat exchange ventilation device |
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Also Published As
Publication number | Publication date |
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CN102414533A (en) | 2012-04-11 |
JPWO2010125643A1 (en) | 2012-10-25 |
TW201038906A (en) | 2010-11-01 |
US20120037349A1 (en) | 2012-02-16 |
TWI421460B (en) | 2014-01-01 |
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