WO2010125643A1 - 熱交換素子 - Google Patents

熱交換素子 Download PDF

Info

Publication number
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
Authority
WO
WIPO (PCT)
Prior art keywords
plate material
heat exchange
corrugated
corrugated plate
flow path
Prior art date
Application number
PCT/JP2009/058361
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
勝 高田
一 外川
秀元 荒井
孝典 今井
全 土井
邦彦 加賀
健 篠崎
Original Assignee
三菱電機株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2011511212A priority Critical patent/JPWO2010125643A1/ja
Priority to CN2009801589877A priority patent/CN102414533A/zh
Priority to US13/265,003 priority patent/US20120037349A1/en
Priority to PCT/JP2009/058361 priority patent/WO2010125643A1/ja
Priority to TW098119195A priority patent/TWI421460B/zh
Publication of WO2010125643A1 publication Critical patent/WO2010125643A1/ja

Links

Images

Classifications

    • 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
    • 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.

Landscapes

  • 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)
PCT/JP2009/058361 2009-04-28 2009-04-28 熱交換素子 WO2010125643A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2011511212A JPWO2010125643A1 (ja) 2009-04-28 2009-04-28 熱交換素子
CN2009801589877A CN102414533A (zh) 2009-04-28 2009-04-28 热交换元件
US13/265,003 US20120037349A1 (en) 2009-04-28 2009-04-28 Heat exchange element
PCT/JP2009/058361 WO2010125643A1 (ja) 2009-04-28 2009-04-28 熱交換素子
TW098119195A TWI421460B (zh) 2009-04-28 2009-06-09 Heat exchange element

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/058361 WO2010125643A1 (ja) 2009-04-28 2009-04-28 熱交換素子

Publications (1)

Publication Number Publication Date
WO2010125643A1 true WO2010125643A1 (ja) 2010-11-04

Family

ID=43031810

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/058361 WO2010125643A1 (ja) 2009-04-28 2009-04-28 熱交換素子

Country Status (5)

Country Link
US (1) US20120037349A1 (zh)
JP (1) JPWO2010125643A1 (zh)
CN (1) CN102414533A (zh)
TW (1) TWI421460B (zh)
WO (1) WO2010125643A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020003411A1 (ja) * 2018-06-27 2020-01-02 株式会社Ｗｅｌｃｏｎ 熱輸送デバイスおよびその製造方法
WO2021059877A1 (ja) * 2019-09-24 2021-04-01 住友精密工業株式会社 熱交換器

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11199365B2 (en) * 2014-11-03 2021-12-14 Hamilton Sundstrand Corporation Heat exchanger
US10557671B2 (en) * 2015-01-16 2020-02-11 Hamilton Sundstrand Corporation Self-regulating heat exchanger
US10727552B2 (en) * 2015-11-04 2020-07-28 Ford Global Technologies, Llc Heat exchanger plate for electrified vehicle battery packs
US20200166293A1 (en) * 2018-11-27 2020-05-28 Hamilton Sundstrand Corporation Weaved cross-flow heat exchanger and method of forming a heat exchanger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02238293A (ja) * 1989-03-10 1990-09-20 Daikin Ind Ltd 熱交換装置
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
JP2006064342A (ja) * 2004-08-30 2006-03-09 Nitta Ind Corp 熱交換素子

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2112743A (en) * 1933-08-15 1938-03-29 Gen Electric Heat transmitting element
US2640194A (en) * 1948-07-16 1953-05-26 Separator Ab Plate heat exchanger
JPS5415973B2 (zh) * 1972-05-08 1979-06-19
SE7509633L (sv) * 1975-02-07 1976-08-09 Terence Peter Nicholson Anordning vid plattvermevexlare
US4293033A (en) * 1979-06-29 1981-10-06 Linde Aktiengesellschaft Plate-type heat exchanger
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
JP3546574B2 (ja) * 1996-01-08 2004-07-28 三菱電機株式会社 熱交換器
JPH1054691A (ja) * 1996-08-08 1998-02-24 Mitsubishi Electric Corp 熱交換器の間隔板及び熱交換器用部材及び熱交換器並びにその製造方法
CA2283089C (en) * 1999-05-10 2004-05-25 Mitsubishi Denki Kabushiki Kaisha Heat exchanger and method for preparing it
WO2001027552A1 (en) * 1999-10-08 2001-04-19 Carrier Corporation A plate-type heat exchanger
JP3969064B2 (ja) * 2001-11-16 2007-08-29 三菱電機株式会社 熱交換器及び熱交換換気装置
JP4206894B2 (ja) * 2003-10-15 2009-01-14 三菱電機株式会社 全熱交換素子
CN2758686Y (zh) * 2004-11-15 2006-02-15 华南理工大学 一种交叉波纹板式膜全热交换强化结构
US7320361B2 (en) * 2005-10-28 2008-01-22 Mitsubishi Denki Kabushiki Kaisha Heat exchanger
CN101233381B (zh) * 2006-10-03 2010-06-09 三菱电机株式会社 总热交换元件及总热交换器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02238293A (ja) * 1989-03-10 1990-09-20 Daikin Ind Ltd 熱交換装置
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
JP2006064342A (ja) * 2004-08-30 2006-03-09 Nitta Ind Corp 熱交換素子

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020003411A1 (ja) * 2018-06-27 2020-01-02 株式会社Ｗｅｌｃｏｎ 熱輸送デバイスおよびその製造方法
JPWO2020003411A1 (ja) * 2018-06-27 2021-03-18 株式会社Ｗｅｌｃｏｎ 熱輸送デバイスおよびその製造方法
JP7207763B2 (ja) 2018-06-27 2023-01-18 株式会社Welcon 熱輸送デバイスおよびその製造方法
WO2021059877A1 (ja) * 2019-09-24 2021-04-01 住友精密工業株式会社 熱交換器
EP4036508A4 (en) * 2019-09-24 2022-11-16 Sumitomo Precision Products Co., Ltd. HEAT EXCHANGER
JP7358152B2 (ja) 2019-09-24 2023-10-10 住友精密工業株式会社 熱交換器

Also Published As

Publication number Publication date
CN102414533A (zh) 2012-04-11
JPWO2010125643A1 (ja) 2012-10-25
TWI421460B (zh) 2014-01-01
US20120037349A1 (en) 2012-02-16
TW201038906A (en) 2010-11-01

Similar Documents

Publication Publication Date Title
WO2010125644A1 (ja) 全熱交換素子
WO2010125643A1 (ja) 熱交換素子
CN105339752B (zh) 具有性能增强部件的流体管道以及包括所述流体管道的装置
JP4816517B2 (ja) 熱交換素子
JP5872859B2 (ja) 熱交換器
JP2017537287A (ja) 熱交換器、熱交換モジュール、熱交換装置、及び熱源ユニット
CN103868380A (zh) 一种板式热交换器
WO2013001744A1 (ja) フィンチューブ型熱交換器
JP6199982B2 (ja) ガスケット及び組立体
JP4504092B2 (ja) プレート式熱交換器
US20160265854A1 (en) Compact stacked fin heat exchanger
WO2020003411A1 (ja) 熱輸送デバイスおよびその製造方法
JP5414502B2 (ja) プレート式熱交換器及びヒートポンプ装置
JP4466156B2 (ja) 熱交換器
CN110530190A (zh) 集管箱及换热器
KR101149983B1 (ko) 용접식 판형 열교환기
WO2020003412A1 (ja) 熱輸送デバイスおよびその製造方法
JP6695495B2 (ja) 全熱交換素子、全熱交換素子の製造方法および全熱交換装置
JP6422585B2 (ja) プレート式熱交換器
CN214666291U (zh) 换热翅片和换热装置
CN213631708U (zh) 高粘度流体用冷却器
CN212511764U (zh) 空调用热交换芯
US20230069888A1 (en) Heat transfer plate and heat exchange element
EP3015809B1 (en) A plate heat exchanger
WO2023217205A1 (zh) 一种换热器

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200980158987.7

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09843987

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2011511212

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 13265003

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 09843987

Country of ref document: EP

Kind code of ref document: A1