WO2011096324A1 - 熱交換器 - Google Patents

熱交換器 Download PDF

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Publication number
WO2011096324A1
WO2011096324A1 PCT/JP2011/051617 JP2011051617W WO2011096324A1 WO 2011096324 A1 WO2011096324 A1 WO 2011096324A1 JP 2011051617 W JP2011051617 W JP 2011051617W WO 2011096324 A1 WO2011096324 A1 WO 2011096324A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
exhaust gas
heat exchanger
exchange tubes
heat
Prior art date
Application number
PCT/JP2011/051617
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
直毅 鹿園
庸人 和氣
四郎 生田
勇 神取
和明 岩元
Original Assignee
国立大学法人東京大学
有限会社和氣製作所
有限会社カンドリ工業
株式会社エム・ケー販売
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 国立大学法人東京大学, 有限会社和氣製作所, 有限会社カンドリ工業, 株式会社エム・ケー販売 filed Critical 国立大学法人東京大学
Priority to CN201180007929.1A priority Critical patent/CN102822617B/zh
Priority to US13/575,727 priority patent/US20130032320A1/en
Publication of WO2011096324A1 publication Critical patent/WO2011096324A1/ja

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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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases

Definitions

  • the present invention relates to a heat exchanger, and more particularly to a finless heat exchanger that recovers heat of exhaust gas by exchanging heat between the exhaust gas after combustion and a heat exchange medium.
  • cooling water is made to flow through a plurality of tubes formed in a U-shape, and substantially orthogonal to the cooling water in the plurality of tubes from the side close to the cooling water outlet of the plurality of tubes.
  • a plurality of tubes and the like are formed of stainless steel to prevent corrosion due to exhaust gas, and heat exchange efficiency is improved by inserting corrugated fins between the plurality of tubes.
  • the heat exchange efficiency may be reduced due to condensed water generated by heat exchange of the exhaust gas.
  • the heat exchanger is downsized by flattening the tubes and reducing the spacing between the tubes to increase the efficiency of heat exchange with the exhaust gas. This hinders the flow of exhaust gas and reduces the efficiency of heat exchange.
  • the fins impede drainage of condensed water, and thus a decrease in heat exchange efficiency becomes significant.
  • the main purpose of the heat exchanger of the present invention is to reduce the size of the heat exchanger and improve the efficiency of heat exchange in a latent heat recovery heat exchanger that recovers the heat of exhaust gas.
  • the heat exchanger of the present invention employs the following means in order to achieve the main object described above.
  • the heat exchanger of the present invention is A finless heat exchanger for recovering heat of the exhaust gas by heat exchange between the exhaust gas after combustion and the heat exchange medium, A plurality of heat exchange tubes formed as a flat tube by a metal plate material excellent in corrosion resistance to acid and arranged in parallel so that the longitudinal direction is mainly the vertical direction; A shell that houses the plurality of heat exchange tubes and forms a flow path for circulating the exhaust gas between the plurality of heat exchange tubes; With The plurality of heat exchange tubes have an inlet for the heat exchange medium formed vertically downward and an outlet for the heat exchange medium formed vertically upward, The shell is formed with the exhaust gas inlet formed vertically above and the exhaust gas outlet formed vertically below, The plurality of heat exchange tubes and / or the shell are formed with meandering guide portions so that the exhaust gas meanders from vertically above to below and flows into gaps between the plurality of heat exchange tubes. This is the gist.
  • a plurality of heat exchange tubes formed as flat tubes with metal plates having excellent corrosion resistance against acid are arranged in parallel so that the longitudinal direction is mainly the vertical direction, and the plurality of arranged heats Place the replacement tube in the shell.
  • a flow path for circulating the exhaust gas is formed between the shell and the plurality of heat exchange tubes.
  • the heat exchange medium inlet is formed vertically below the plurality of heat exchange tubes, the heat exchange medium outlet is formed vertically upward, and the exhaust gas inlet is formed vertically upward on the shell.
  • An exhaust port for exhaust gas is formed.
  • a meandering guide portion is formed in one or both of the plurality of heat exchange tubes or shells so that the exhaust gas meanders vertically from below to flow through the gaps of the plurality of heat exchange tubes.
  • the heat exchange medium flows vertically from the inlet formed in the vertically lower side of the plurality of heat exchange tubes, and vertically moves the plurality of heat exchange tubes arranged in parallel. From the outflow port formed vertically above the plurality of heat exchange tubes.
  • the exhaust gas flows from the inlet formed vertically above the shell, flows through the flow path formed between the shell and the plurality of heat exchange tubes, and flows from the outlet formed vertically below the shell. leak.
  • the exhaust gas is meandered vertically upward from below by a meandering guide portion formed in one or both of the plurality of heat exchange tubes or shells.
  • the heat exchange medium flows vertically downward from above, and the exhaust gas meanders by the meandering guide portion, but as a whole it flows from vertically upward to vertically downward.
  • Exchange efficiency will be improved.
  • Condensed water is generated on the flat surfaces of the plurality of heat exchange tubes due to heat exchange of the exhaust gas, but the plurality of heat exchange tubes are arranged in parallel so that the longitudinal direction is mainly the vertical direction. Drained while collecting water. As a result, it is possible to suppress the generated condensed water from remaining and hinder the flow of the exhaust gas, and reduce the pressure loss of the exhaust gas.
  • the heat exchanger of the present invention is configured as a finless heat exchanger, it promotes drainage of condensed water as compared with a case where fins are attached between a plurality of heat exchange tubes. Can do. As a result, it is possible to provide a heat exchanger that is small in size and efficient in heat exchange.
  • the plurality of heat exchange tubes may be formed with a vertical groove formed at substantially the center of the flat surface.
  • the condensed water generated on the flat surfaces of the plurality of heat exchange tubes flows vertically downward along the groove, so that the drainage of the condensed water can be improved, and heat that is more compact and efficient in heat exchange can be obtained.
  • It can be an exchanger.
  • the strength of the plurality of heat exchange tubes can be improved by forming this groove.
  • a plurality of heat exchange tubes can be formed using a thinner metal plate.
  • the plurality of heat exchange tubes may be configured such that the grooves are bonded and fixed inside. In this way, the strength of the plurality of heat exchange tubes can be further improved.
  • the meandering guide portion is a guide wall formed inside the shell so that the exhaust gas flows in a substantially horizontal direction with respect to the plurality of heat exchange tubes.
  • the meandering guide portion is a rib formed on the flat surface of the plurality of heat exchange tubes in the direction of the guide wall at a position aligned with the guide wall of the shell, in addition to the guide wall. It can also be. If it carries out like this, exhaust gas can be made to flow through the clearance gap between several tubes for heat exchange, meandering more reliably, and the efficiency of heat exchange can be improved.
  • the meandering guide portion is a plurality of ribs formed in a substantially horizontal direction on a flat surface of the plurality of heat exchange tubes, and the shell includes an outer wall.
  • the shell includes an outer wall.
  • the plurality of ribs and shells formed on the flat surfaces of the plurality of heat exchange tubes allow the gaps between the plurality of heat exchange tubes while meandering the exhaust gas without forming a guide wall inside the shell.
  • the efficiency of heat exchange can be improved.
  • the plurality of heat exchanging tubes may be formed by continuously forming concave and convex portions that are bent at an angle within a range of 10 degrees to 80 degrees with respect to a main flow direction of the exhaust gas. It is also possible to form a plurality of wavy uneven portions formed of a portion over substantially one surface. When the exhaust gas flows through the gaps between the plurality of heat exchange tubes, the exhaust gas flows along with the secondary flow by the plurality of wavy uneven portions formed on the flat surfaces of the plurality of heat exchange tubes. As a result, the heat exchange efficiency is improved.
  • the concave portion of the wavy uneven portion plays a role of the drainage flow path of the condensed water. That is, the drainage of condensed water can be improved by forming a plurality of wave-shaped uneven portions on the flat surfaces of a plurality of heat exchange tubes.
  • the plurality of heat exchange tubes are the wave-shaped unevenness at a portion located vertically above the flat surface.
  • the angle of the portion with respect to the main flow direction of the exhaust gas is formed to be smaller than the angle with respect to the main flow direction of the exhaust gas of the wavy uneven portion in a portion located vertically below the flat surface. You can also.
  • the secondary flow of the exhaust gas is promoted, and the exhaust gas and the heat exchange medium
  • the efficiency of heat exchange can be improved, and by increasing the angle of the wavy irregularities in the portion located vertically below the flat surface of the plurality of heat exchange tubes with respect to the main flow direction of the exhaust gas, The angle of the recess with respect to the vertical direction can be reduced to make it easier for the condensed water to flow vertically downward.
  • the plurality of heat exchanging tubes have an angle with respect to the main flow direction of the exhaust gas at the portion located vertically above the flat surface in the range of 10 to 45 degrees and the flat surface It is also possible that the angle of the wavy uneven portion at a portion located vertically below the main flow direction of the exhaust gas is within a range of 45 degrees to 80 degrees.
  • FIG. It is a block diagram which shows the outline of a structure of the heat exchanger 20 as one Example of this invention. It is a side view which shows the external appearance of the several tube 30 for heat exchange used for the heat exchanger 20 of an Example from the side. 4 is an enlarged explanatory view showing a part of a heat exchange tube 30 in an enlarged manner.
  • FIG. It is explanatory drawing which shows typically the flow of the exhaust gas in the heat exchanger 20 of an Example.
  • FIG. 1 is a configuration diagram showing an outline of the configuration of a heat exchanger 20 as an embodiment of the present invention
  • FIG. 2 is a side view of the appearance of a plurality of heat exchange tubes 30 used in the heat exchanger 20 of the embodiment.
  • FIG. 3 is an enlarged explanatory view showing a part of the heat exchange tube 30 in an enlarged manner.
  • the heat exchanger 20 according to the embodiment is configured as a finless heat exchanger that recovers the heat of exhaust gas by exchanging heat between the exhaust gas after combustion and a heat exchange medium such as cooling water. Is provided with a plurality of (for example, 22) heat exchange tubes 30 arranged in parallel so as to be in the vertical direction, and a shell 40 that houses the plurality of heat exchange tubes 30.
  • Each of the heat exchange tubes 30 is a plate material having a thickness of 0.3 mm made of a metal material (for example, stainless steel) excellent in acid resistance to acid, and has a height (length) of 150 mm, a width of 30 mm, and an inner heat exchange medium.
  • a heat exchange medium inlet 31 is formed in the vicinity of the lower end of each heat exchange tube 30 in the vertical direction, and each inlet 31 of each heat exchange tube 30 communicates with a communication pipe 31a.
  • a heat exchange medium outlet 32 is formed in the vicinity of the upper upper end of each heat exchange tube 30 vertically, and each outlet 32 of each heat exchange tube 30 communicates with a communication pipe 32a. Therefore, the heat exchange medium flows in from each inlet 31 located vertically below each heat exchange tube 30, flows vertically through each heat exchange tube 30, and is located above each heat exchange tube 30 vertically. It flows out from each outflow port 32.
  • a convex groove 36 is formed in the center of the flat surface of each heat exchange tube 30 with a vertical depth of 1.2 mm and a width of 1.6 mm. ing. Since the grooves 36 are formed on both flat surfaces of the heat exchanging tube 30, the grooves 36 of both flat surfaces abut on the inside of the tube. In the embodiment, the grooves 36 on both flat surfaces that are in contact with the inside of the tube are bonded and fixed by brazing or the like. Thereby, the intensity
  • each heat exchange tube 30 has a concave portion 33 having a shape in which a continuous “V” or “W” shape is bent by a predetermined angle ⁇ with respect to the horizontal and rotated by 90 degrees.
  • wavy rugged portions 33 and 34 each including a convex portion 34 are formed on the entire surface.
  • the horizontal angle ⁇ of the wavy uneven portions 33 and 34 is in the range of 10 to 80 degrees, preferably in the range of 30 to 60 degrees, and more preferably in the range of 30 to 45 degrees. Degree.
  • the wavy uneven portions 33 and 34 formed on the flat surface of each heat exchange tube 30 cause a secondary flow in addition to the main flow of the exhaust gas when the exhaust gas flows substantially horizontally.
  • the efficiency of heat exchange between the exhaust gas and the heat exchange medium can be improved.
  • the wavy uneven portions 33 and 34 collect condensed water adhering to the flow of the exhaust gas and the effect of surface tension in the recessed portion 33 and further guide it vertically downward, thereby improving the drainage of the condensed water. Can do.
  • the shell 40 is made of a plurality of heat connected by connecting pipes 31 a and 32 a with a plate material having a thickness of 0.3 mm made of a metal material (for example, stainless steel) having excellent corrosion resistance against acid. It is formed as a substantially rectangular parallelepiped case that houses the replacement tube 30, and exhaust gas flow paths 46 a, 46 b, 46 c, 46 d are formed between the plurality of heat exchange tubes 30.
  • An exhaust gas inlet 41 is formed on the left side in FIG. 1 vertically above the shell 40, and an exhaust gas outlet 42 is formed on the right side in FIG.
  • a plurality of substantially rectangular heat exchange tubes 30 formed as flat tubes are arranged in parallel at intervals of 1.6 mm so that the longitudinal direction is the vertical direction.
  • the heat exchange medium flows in from the inlets 31 located vertically below, the tubes 30 for heat exchange flow vertically upward, and flow out from the outlets 32 located vertically above the tubes 30 for heat exchange,
  • exhaust gas flows in from an inlet 41 formed vertically above the shell 40, and flow paths 46a, 46b, 46c, 46d formed by the shell 40, a plurality of heat exchange tubes 30, and guide walls 43, 44.
  • the plurality of heat exchange tubes 30 while meandering and flowing out from an outlet 42 formed vertically below the shell 40, thereby exhaust gas and the plurality of heat exchange tubes 3.
  • the plurality of heat exchange tubes 30 As counterflow as a whole heat exchange medium flowing through, it is possible to improve the efficiency of heat exchange.
  • the plurality of heat exchange tubes 30 By arranging the plurality of heat exchange tubes 30 in parallel so that the longitudinal direction is the vertical direction, the condensed water generated on the flat surfaces of the plurality of heat exchange tubes 30 by the heat exchange of the exhaust gas is collected vertically downward. It can be drained while. As a result, it is possible to suppress the generated condensed water from remaining and hinder the flow of the exhaust gas, and reduce the pressure loss of the exhaust gas.
  • the heat exchanger 20 according to the embodiment is configured as a finless heat exchanger, the condensate drainage is promoted as compared with the case where fins are attached between the plurality of heat exchange tubes 30. Can do. As a result, it is possible to provide a heat exchanger that is small in size and efficient in heat exchange.
  • the flat surface of the tube 30 for heat exchange by heat exchange of waste gas.
  • the condensate produced in the water can be collected and guided vertically downward, the drainage of the condensate can be improved, the strength of the plurality of heat exchange tubes 30 can be improved, and the thin plate thickness
  • a plurality of heat exchange tubes 30 can be formed of a metal material, and a smaller heat exchanger can be obtained.
  • the strength of the heat exchanging tube 30 can be further improved by bonding and fixing the groove 36 inside the tube.
  • the recessed part 33 and convex part which bend
  • a secondary flow can be generated, and as a result, the efficiency of heat exchange between the exhaust gas and the heat exchange medium can be improved.
  • the wavy uneven portions 33 and 34 collect condensed water adhering to the flow of exhaust gas in the recessed portion 33 and guide it vertically downward, it is possible to further improve the drainage of the condensed water.
  • the groove 36 is formed at the center of the flat surface of the plurality of heat exchange tubes 30 and the wavy uneven portions 33 and 34 are formed on substantially the entire flat surface.
  • the groove 36 is formed in the center of the flat surface of the plurality of heat exchange tubes 30B, but the wavy uneven portions 33 and 34 may not be formed on the flat surface.
  • the groove 36 is not formed at the center of the flat surface of the plurality of heat exchange tubes 30C, but the wavy uneven portions 33C and 34C are formed on the flat surface. It is good also as what to do.
  • the wavy uneven portions 33C and 34C may be formed at the center of the flat surface of the plurality of heat exchange tubes 30C.
  • neither the groove 36 nor the wavy uneven portions 33 and 34 may be formed on the flat surfaces of the plurality of heat exchange tubes.
  • the groove 36 is formed in the center of the flat surface of the plurality of heat exchange tubes 30 and the wavy uneven portions 33 and 34 are formed on substantially the entire flat surface.
  • ribs 37a to 37d protruding outward may be formed at positions aligned with the flat guide walls 43 and 44 of the plurality of heat exchange tubes 30D. . By so doing, it is possible to more reliably induce exhaust gas meandering. In this case, it is preferable that the adjacent ribs 37a and 37b and the ribs 37c and 37d are separated by the groove 36.
  • the angle ⁇ from the horizontal of the wavy uneven portions 33 and 34 formed on the flat surface is set to 30 degrees, but is in the range of 10 degrees to 80 degrees. And preferably in the range of 30 to 60 degrees.
  • the wavy irregularities 33Fa and 34Fa located on the exhaust gas inflow side have a small angle ⁇ from the horizontal, and the wavy irregularities located on the exhaust gas outflow side.
  • the angle ⁇ from the horizontal may be larger than the angle ⁇ .
  • the angle ⁇ is preferably 10 to 45 degrees, and the angle ⁇ is preferably 45 to 80 degrees.
  • 30 degrees was used for the angle ⁇ , and 60 degrees was used for the angle ⁇ .
  • an angle ⁇ is set so as to improve the efficiency of heat exchange by promoting the secondary flow of the exhaust gas, and the wavy shape located on the exhaust gas outflow side.
  • the uneven portions 33Fb and 34Fb are based on setting the angle ⁇ so as to promote the drainage of the condensed water downward. Accordingly, the wavy uneven portions 33 and 34 may be formed so that the angle from the horizontal increases stepwise or stepwise from the inflow side to the outflow side of the exhaust gas.
  • the plurality of heat exchange tubes 30 are made of a stainless steel plate having a thickness of 0.3 mm, the height (length) is 150 mm, the width is 30 mm, and the flow path of the inner heat exchange medium
  • the thickness of the tube is 2.4 mm (the total thickness is 3.0 mm including the plate thickness) so that it becomes a substantially rectangular flat tube as a whole, and the gap between the adjacent heat exchange tubes 30 is 1.6 mm.
  • any plate material may be used as long as it is a metal material having excellent corrosion resistance against acids other than stainless steel, and the thickness of the plate material maintains strength. If possible, it may be thinner than 0.3 mm or thicker.
  • the height, width, and thickness of the inner heat exchange medium flow path are not limited to 150 mm, 30 mm, and 2.4 mm, and any thickness may be used as long as the inner heat exchange medium flow path thickness is 3 mm or less. It may be the height width and the thickness of the flow path of the inner heat exchange medium.
  • the shape of the plurality of heat exchange tubes 30 may not be a substantially rectangular flat hollow tube, and may be, for example, an elliptical flat hollow tube.
  • the gap between the adjacent heat exchange tubes 30 is not limited to 1.6 mm, and may be any interval as long as it is 3 mm or less.
  • the plurality of heat exchange tubes 30 do not need to be arranged in parallel so that the longitudinal direction is accurately in the vertical direction, and may be arranged in parallel so that the longitudinal direction is in the vertical direction at a certain angle.
  • the shell 40 is formed as a substantially rectangular parallelepiped case that houses a plurality of heat exchange tubes 30 by using a stainless steel plate having a thickness of 0.3 mm.
  • the shell 40 is resistant to acids other than stainless steel. Any plate material may be used as long as it is a plate material made of an excellent metal material, and the thickness of the plate material may be less than 0.3 mm or thick as long as the strength can be maintained.
  • the shell 40 is formed as a substantially rectangular parallelepiped case that houses the plurality of heat exchange tubes 30, and a plurality of exhaust gases meander while providing guide walls 43 and 44 inside thereof.
  • the heat exchange tube 30 flows through the gaps and the flow paths 46a, 46b, 46c, and 46d, as shown in the heat exchanger 20G of the modified example of FIG. 10, a plurality of ribs 37a to 37d are formed.
  • the heat exchange tube 30D is used, and the shell 40G is formed on the side surface of the outer wall where the ribs 37a of the plurality of heat exchange tubes 30D are formed and the side surface where the ribs 37d of the plurality of heat exchange tubes 30D are formed.
  • the plurality of ribs 37a to 37d of the plurality of heat exchange tubes 30D are crossed from the uppermost side to the lower side of the both side surfaces.
  • the plurality of ribs 37a to 37d and the shell 40G formed on the flat surfaces of the plurality of heat exchange tubes 30D and the plurality of ribs 37a to 37d and the shell 40G form a plurality of exhaust gases while meandering the exhaust gas.
  • the heat exchange tube 30D can be passed through the gap, and the efficiency of heat exchange can be improved.
  • the present invention can be used in the heat exchanger manufacturing industry.
PCT/JP2011/051617 2010-02-02 2011-01-27 熱交換器 WO2011096324A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180007929.1A CN102822617B (zh) 2010-02-02 2011-01-27 换热器
US13/575,727 US20130032320A1 (en) 2010-02-02 2011-01-27 Heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010021027A JP5620685B2 (ja) 2010-02-02 2010-02-02 熱交換器
JP2010-021027 2010-02-02

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WO2011096324A1 true WO2011096324A1 (ja) 2011-08-11

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US (1) US20130032320A1 (zh)
JP (1) JP5620685B2 (zh)
CN (1) CN102822617B (zh)
WO (1) WO2011096324A1 (zh)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6266228B2 (ja) * 2013-05-13 2018-01-24 三菱電機ビルテクノサービス株式会社 熱交換器
JP6367601B2 (ja) * 2014-04-23 2018-08-01 京セラ株式会社 燃料電池装置
JP6459027B2 (ja) * 2014-07-15 2019-01-30 国立大学法人 東京大学 熱交換器
CN108700384A (zh) * 2015-12-28 2018-10-23 国立大学法人东京大学 换热器
CN105674789B (zh) * 2016-01-19 2018-01-19 昆明五威科工贸有限公司 一种水箱
JP6615316B2 (ja) * 2016-03-16 2019-12-04 三菱電機株式会社 フィンレス型の熱交換器、そのフィンレス型の熱交換器を備えた空気調和機の室外機、及びそのフィンレス型の熱交換器を備えた空気調和機の室内機
DK3290822T3 (da) * 2016-08-30 2020-02-24 Alfa Laval Corp Ab Pladevarmeveksler til solvarme
JP6717326B2 (ja) * 2017-07-18 2020-07-01 株式会社デンソー 熱交換器
CN112648874B (zh) * 2020-12-26 2022-07-15 国网甘肃省电力公司经济技术研究院 一种基于阶梯式相变管束的储热与释热装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54111156A (en) * 1978-02-21 1979-08-31 Nippon Dyeing Machine Mfg Co Plate type heat exchanger
JPH06123578A (ja) * 1992-10-09 1994-05-06 Mitsubishi Heavy Ind Ltd 積層型熱交換器
JP2001183031A (ja) * 1999-12-27 2001-07-06 Mitsubishi Heavy Ind Ltd 熱交換器、吸収冷凍機、及び、コジェネレーションシステム
JP2004177061A (ja) * 2002-11-28 2004-06-24 Toyo Radiator Co Ltd 排ガス冷却用熱交換器のウェーブフィン
JP2007278637A (ja) * 2006-04-10 2007-10-25 Xenesys Inc 熱交換器
JP2008082579A (ja) * 2006-09-26 2008-04-10 Kyocera Corp プレートフィン型熱交換器および燃料電池システム
JP2009519431A (ja) * 2005-12-14 2009-05-14 キョントン ナビエン カンパニー リミテッド 暖房および温水供給用凝縮ボイラの熱交換器

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10318695A (ja) * 1997-05-19 1998-12-04 Zexel Corp 熱交換器
DE19846518B4 (de) * 1998-10-09 2007-09-20 Modine Manufacturing Co., Racine Wärmetauscher, insbesondere für Gase und Flüssigkeiten
SE521816C2 (sv) * 1999-06-18 2003-12-09 Valeo Engine Cooling Ab Fluidtransportrör samt fordonskylare med sådant
CN2404088Y (zh) * 2000-01-31 2000-11-01 曹毅文 导槽板高效换热器
DE10214467A1 (de) * 2002-03-30 2003-10-09 Modine Mfg Co Abgaswärmetauscher für Kraftfahrzeuge
DE10247264A1 (de) * 2002-10-10 2004-04-29 Behr Gmbh & Co. Plattenwärmeübertrager in Stapelbauweise
JP3956885B2 (ja) * 2003-04-03 2007-08-08 株式会社デンソー 熱交換器用チューブの製造方法及び装置
JP2008516176A (ja) * 2004-10-07 2008-05-15 ベール ゲーエムベーハー ウント コー カーゲー 空気冷却される排ガス熱伝達体、特に自動車のための排ガスクーラー
EP1657512B2 (de) * 2004-11-10 2010-06-16 Modine Manufacturing Company Wärmetauscher mit offenem Profil als Gehäuse
EP1817534B1 (fr) * 2004-11-30 2009-12-02 Valeo Systemes Thermiques Sas Echangeur de chaleur avec accumulateur thermique
US7182128B2 (en) * 2005-03-09 2007-02-27 Visteon Global Technologies, Inc. Heat exchanger tube having strengthening deformations
EP1994352A4 (en) * 2006-01-19 2010-06-02 Modine Mfg Co FLAT TUBE, FLAT TUBE HEAT EXCHANGER AND MANUFACTURING METHOD THEREFOR
CN101400959B (zh) * 2006-03-16 2010-09-29 贝洱两合公司 用于汽车的热交换器
DE102006048305B4 (de) * 2006-10-12 2011-06-16 Modine Manufacturing Co., Racine Plattenwärmetauscher
EP2122289A4 (en) * 2007-02-27 2013-01-09 Carrier Corp MULTI-CHANNEL FLAT TUBE EVAPORATOR WITH ENHANCED CONDENSATE EXHAUST

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54111156A (en) * 1978-02-21 1979-08-31 Nippon Dyeing Machine Mfg Co Plate type heat exchanger
JPH06123578A (ja) * 1992-10-09 1994-05-06 Mitsubishi Heavy Ind Ltd 積層型熱交換器
JP2001183031A (ja) * 1999-12-27 2001-07-06 Mitsubishi Heavy Ind Ltd 熱交換器、吸収冷凍機、及び、コジェネレーションシステム
JP2004177061A (ja) * 2002-11-28 2004-06-24 Toyo Radiator Co Ltd 排ガス冷却用熱交換器のウェーブフィン
JP2009519431A (ja) * 2005-12-14 2009-05-14 キョントン ナビエン カンパニー リミテッド 暖房および温水供給用凝縮ボイラの熱交換器
JP2007278637A (ja) * 2006-04-10 2007-10-25 Xenesys Inc 熱交換器
JP2008082579A (ja) * 2006-09-26 2008-04-10 Kyocera Corp プレートフィン型熱交換器および燃料電池システム

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JP2011158200A (ja) 2011-08-18

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