US20130032320A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20130032320A1
US20130032320A1 US13/575,727 US201113575727A US2013032320A1 US 20130032320 A1 US20130032320 A1 US 20130032320A1 US 201113575727 A US201113575727 A US 201113575727A US 2013032320 A1 US2013032320 A1 US 2013032320A1
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US
United States
Prior art keywords
heat
exhaust gas
exchange tubes
exchange
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US13/575,727
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English (en)
Inventor
Naoki Shikazono
Tsunehito Wake
Shiro Ikuta
Isamu Kandori
Kazuaki Iwamoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KANDORI INDUSTRY
KANDORI INDUSTRY Ltd
University of Tokyo NUC
Waki Factory Inc
KANDORI IND Ltd
Original Assignee
University of Tokyo NUC
Waki Factory Inc
MK Sale Co Ltd
KANDORI IND Ltd
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 University of Tokyo NUC, Waki Factory Inc, MK Sale Co Ltd, KANDORI IND Ltd filed Critical University of Tokyo NUC
Assigned to UNIVERSITY OF TOKYO, THE, M K SALE CO., LTD., WAKI FACTORY INC., KANDORI INDUSTRY LTD. reassignment UNIVERSITY OF TOKYO, THE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IWAMOTO, KAZUAKI, WAKE, TSUNEHITO, SHIKAZONO, NAOKI, KANDORI, ISAMU, IKUTA, SHIRO
Publication of US20130032320A1 publication Critical patent/US20130032320A1/en
Assigned to THE UNIVERSITY OF TOKYO, WAKI FACTORY INC., KANDORI INDUSTRY reassignment THE UNIVERSITY OF TOKYO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: M K SALE CO., LTD.
Abandoned legal-status Critical Current

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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 specifically relates to a finless heat exchanger that recovers heat of exhaust gas, which results from combustion, via heat exchange with a heat exchange medium.
  • the heat exchange efficiency may be lowered by condensed water resulting from heat exchange with the exhaust gas.
  • a heat exchanger is downsized by flattening the tubes and reducing the spaces between the tubes to enhance the efficiency of heat exchange with exhaust gas, if the spaces between the tubes are reduced, the condensed water remains between the tubes, hindering the flow of the exhaust gas, which results in a decrease in heat exchange efficiency.
  • the fins hinder discharge of condensed water, resulting in a significant decrease in heat exchange efficiency in addition to a decrease in fin efficiency.
  • a main object of a heat exchanger according to the present invention is to achieve downsizing and enhancement of heat exchange efficiency of a heat exchanger for a heat exchanger for latent heat recovery, which recovers heat of exhaust gas.
  • the present invention accomplishes at least part of the demands mentioned above and the other relevant demands by the following configurations applied to the heat exchanger.
  • the present invention is directed to a finless heat exchanger for recovering heat of exhaust gas resulting from combustion via heat exchange between the exhaust gas and a heat exchange medium.
  • the heat exchanger includes a plurality of heat-exchange tubes each formed as a flat pipe using a metal plate material having an excellent acid corrosion resistance.
  • the plurality of heat-exchange tubes is arranged in parallel in such a manner that each of respective longitudinal directions thereof is mainly a vertical direction.
  • the finless heat exchanger further includes a shell that houses the plurality of heat-exchange tubes and forms a flow path for the exhaust gas to pass therethrough between the plurality of heat-exchange tubes and the shell.
  • the plurality of heat-exchange tubes each include an inlet for the heat exchange medium at a vertically lower portion thereof and an outlet for the heat exchange medium at a vertically upper portion thereof.
  • the shell includes an inlet for the exhaust gas at a vertically upper portion thereof and an outlet for the exhaust gas at a vertically lower portion thereof.
  • the plurality of heat-exchange tubes and/or the shell include a meandering guiding section formed so that the exhaust gas flows in a space between the plurality of heat-exchange tubes while meandering downward from the vertically upper portion.
  • a plurality of heat-exchange tubes each formed as a flat pipe using a metal plate material having an excellent acid corrosion resistance are arranged in parallel in such a manner that each of respective longitudinal directions thereof is mainly a vertical direction, and the plurality of heat-exchange tubes arranged are housed in a shell. Consequently, a flow path for exhaust gas to pass through is formed between the shell and the plurality of heat-exchange tubes.
  • the plurality of heat-exchange tubes each include an inlet for a heat exchange medium at a vertically lower portion thereof and an outlet for the heat exchange medium at a vertically upper portion thereof, and the shell includes an inlet for the exhaust gas at a vertically upper portion thereof and an outlet for the exhaust gas in a vertically lower portion thereof.
  • a meandering guiding section is formed in either or both of the plurality of heat-exchange tubes and the shell so that the exhaust gas flows in spaces between the plurality of heat-exchange tubes while meandering downward from the vertically upper portion.
  • a plurality of heat-exchange tubes formed as flat pipes are arranged in parallel and housed in a shell, enabling provision of a small-size heat exchanger.
  • a heat exchange medium flows in from the inlets formed at the vertically lower portions of the plurality of heat-exchange tubes and flow in the plurality of heat-exchange tubes arranged in parallel from the vertically lower portions to the vertically upper portions, and flows out from the outlets formed at the vertically upper portions of the plurality of heat-exchange tubes.
  • exhaust gas flows in from the inlet formed at the vertically upper portion of the shell, flows in the flow path formed between the shell and the plurality of heat-exchange tubes, and flows out from the outlet formed at the vertically lower portion of the shell.
  • the exhaust gas flows in the spaces between the plurality of heat-exchange tubes while meandering downward from the vertically upper portion via the meandering guiding section formed in either or both of the plurality of heat-exchange tubes and the shell. Accordingly, the heat exchange medium flows from the vertically lower portions to the vertically upper portions, while the exhaust gas flows from the vertically upper portion to the vertically lower portion as a whole although the exhaust gas is made to meander by the meandering guiding section, and thus, the heat exchange medium and the exhaust gas have flows opposed to each other, enhancing the heat exchange efficiency.
  • the plurality of heat-exchange tubes can each include a vertical groove at a substantial center of a flat surface thereof. Consequently, condensed water generated on the flat surfaces of the plurality of heat-exchange tubes flows along the grooves to the vertically lower portions, enabling enhancement of the condensed water discharge performance, and thus, a heat exchanger having a small size and good heat exchange efficiency can be provided. Furthermore, as a result of formation of the grooves, the strength of the plurality of heat-exchanges can be enhanced. Consequently, the plurality of heat-exchange tubes can be formed using a thinner metal plate material. In such case, the groove in each of the plurality of heat-exchange tubes can be fixed by bonding inside the heat-exchange tube. Consequently, the strength of the plurality of heat-exchange tubes can further be enhanced.
  • the meandering guiding section can include a guide wall formed inside the shell so that the exhaust gas flows in a substantially horizontal direction orthogonal to the plurality of heat-exchange tubes.
  • the meandering guiding section can further include a rib formed toward the guide wall at a flat surface of each of the plurality of heat-exchange tubes at a position aligned with the guide wall of the shell, in addition to the guide wall. Consequently, the exhaust gas can be made to more reliably flow in the spaces between the plurality of heat-exchange tubes while meandering, enabling enhancement in heat exchange efficiency.
  • the meandering guiding section can include a plurality of ribs formed at a plurality of positions in a substantially horizontal direction on a flat surface of each of the plurality of heat-exchange tubes, and an inner side of an outer wall of the shell can be in contact with one side surface and another side surface alternately from an uppermost position to a lower position from among opposite side surfaces of the plurality of heat-exchange tubes at positions where the plurality of ribs are formed and is not in contact with a side surface opposite to the side surface that is in contact with the inner side from among opposite side surfaces at a same position.
  • the plurality of ribs formed on the flat surfaces of the heat-exchange tubes and the shell can make the exhaust gas flow in the spaces between the plurality of heat-exchange tubes while meandering without forming guide walls inside the shell, enabling enhancement of the heat exchange efficiency.
  • the plurality of heat-exchange tubes can each include a plurality of wavelike depression-and-projection portions formed over a substantial entirety of a flat surface thereof, each of the plurality of wavelike depression-and-projection portions including a depression portion and a projection portion flexed at an angle ranging from 10 to 80 degrees relative to a main flow direction of the exhaust gas to be continuous with each other.
  • the exhaust gas flows in the spaces between the plurality of heat-exchange tubes, the exhaust gas flows accompanied by a secondary flow caused by the plurality of wavelike depression-and-projection portions formed on the flat surfaces of the plurality of heat-exchange tubes. Consequently, the heat exchange efficiency is enhanced.
  • the condensed water is guided to the depression portions of the wavelike depression-and-projection portions by means of the flow of the exhaust gas and the effect of the surface tension, and thus, the depression portions of the wavelike depression-and-projection portions have the role of a discharge flow path for the condensed water.
  • formation of the wavelike depression-and-projection portions at the flat surfaces of the plurality of heat-exchange tubes enables enhancement of the condensed water discharge performance.
  • the plurality of heat-exchange tubes can be each formed so that an angle of the wavelike depression-and-projection portions in a region positioned in a vertically upper portion of the flat surface relative to the main flow direction of the exhaust gas is smaller than an angle of the wavelike depression-and-projection portions in a region positioned in a vertically lower portion of the flat surface relative to the main flow direction of the exhaust gas.
  • the plurality of heat-exchange tubes can be each formed so that the angle of the wavelike depression-and-projection portions in the region positioned in the vertically upper portion of the flat surface relative to the main flow direction of the exhaust gas falls within a range of 10 to 45 degrees and the angle of the wavelike depression-and-projection portions in the region positioned in the vertically lower portion of the flat surface relative to the main flow direction of the exhaust gas falls within a range of 45 to 80 degrees.
  • FIG. 1 is a configuration diagram illustrating a schematic configuration of a heat exchanger 20 in one embodiment of the invention
  • FIG. 2 is a side view of an outer appearance of a plurality of heat-exchange tubes 30 used in the heat exchanger 20 ;
  • FIG. 3 is an enlarged diagram illustrating a heat-exchange tube 30 with a part thereof enlarged
  • FIG. 4 is a pattern diagram illustrating a flow of an exhaust gas in the heat exchanger 20 of the invention.
  • FIG. 5 schematically illustrates the configuration of another heat exchanger 20 B in one modified example
  • FIG. 6 schematically illustrates the configuration of another heat exchanger 20 C in another modified example
  • FIG. 7 schematically illustrates the configuration of another heat exchanger 20 D in another modified example
  • FIG. 8 schematically illustrates the configuration of another heat exchanger 20 E in another modified example
  • FIG. 9 schematically illustrates the configuration of another heat-exchange tube 30 F in one modified example
  • FIG. 10 schematically illustrates the configuration of another heat exchanger 20 G in one modified example.
  • FIG. 1 is a configuration diagram illustrating a schematic configuration of a heat exchanger 20 , which is an embodiment of the present invention
  • FIG. 2 is a side view of an outer appearance of a plurality of heat-exchange tubes 30 used in the heat exchanger 20 according to the embodiment
  • FIG. 3 is an enlarged diagram illustrating a heat-exchange tube 30 with a part thereof enlarged.
  • the heat exchanger 20 is configured as a finless heat exchanger that recovers heat of exhaust gas resulting from combustion via heat exchange between the exhaust gas and a heat exchange medium such as cooling water, and as illustrated, includes a plurality of (for example, 22) heat-exchange tubes 30 arranged in parallel in such a manner that each of respective longitudinal directions thereof is a vertical direction, and a shell 40 that houses the plurality of heat-exchange tubes 30 .
  • Each heat-exchange tube 30 is formed as a flat pipe using a plate material having a thickness of 0.3 mm and including a metal material having an excellent acid corrosion resistance (for example, stainless steel), the flat pipe having a substantially rectangular shape in its entirety, which has a height (length) of 150 mm, a width of 30 mm and an inner heat exchange medium flow path thickness of 2.4 mm (an entire thickness of 3.0 mm including the thickness of the plate), and is arranged in parallel with an adjacent heat-exchange tube 30 so as to provide a space of 1.6 mm therebetween in such a manner that the longitudinal direction thereof is the vertical direction.
  • a plate material having a thickness of 0.3 mm and including a metal material having an excellent acid corrosion resistance for example, stainless steel
  • the flat pipe having a substantially rectangular shape in its entirety, which has a height (length) of 150 mm, a width of 30 mm and an inner heat exchange medium flow path thickness of 2.4 mm (an entire thickness of 3.0 mm including the thickness of the plate), and is
  • An inlet 31 for a heat exchange medium is formed in the vicinity of a lower end of a vertically lower portion of each heat-exchange tube 30 , and the respective inlets 31 of the respective heat-exchange tubes 30 communicate with one another via a connecting pipe 31 a .
  • an outlet 32 for the heat exchange medium is formed in the vicinity of an upper end of a vertically upper portion of each heat-exchange tube 30 , and the respective outlets 32 of the respective heat-exchange tubes 30 via a connecting pipe 32 a .
  • a heat exchange medium flows in from the respective inlets 31 positioned in the vertically lower portions of the respective heat-exchange tubes 30 , flows in the respective heat-exchange tubes 30 toward the vertically upper portions, and flows out from the respective outlets 32 positioned in the vertically upper portions of the respective heat-exchange tubes 30 .
  • each flat surface of each heat-exchange tube 30 At a center of each flat surface of each heat-exchange tube 30 , as illustrated in FIGS. 1 and 3 , a vertical groove 36 projecting inward, the groove 36 having a depth of 1.2 mm and a width of 1.6 mm is formed. Since the groove 36 is formed in each of the opposite flat surfaces of the heat-exchange tube 30 , the grooves 36 at the opposite flat surfaces are in contact with each other. In the embodiment, the grooves 36 at the opposite flat surfaces, the grooves 36 being in contact with each other inside the tube, are fixed by bonding using, e.g., brazing. Consequently, the strength of the heat-exchange tubes 30 can be enhanced. Furthermore, the grooves 36 each collect condensed water generated on the surfaces of the respective heat-exchange tube 30 as a result of heat exchange with exhaust gas and guide the condensed water to the respective vertically lower portion, enabling enhancement of the condensed water discharge performance.
  • wavelike depression-and-projection portions 33 , 34 each including depression portions 33 and projection portions 34 having a shape formed by making “V” or “W”-shapes be continuous with one another by rotating the “V” or “W”-shapes by 90 degrees, the “V” or “W”-shapes being flexed at a predetermined angle ⁇ relative to a horizontal direction are formed over an entirety of each flat surface of each heat-exchange tube 30 .
  • the angle ⁇ of the wavelike depression-and-projection portions 33 , 34 relative to the horizontal direction falls within a range of 10 to 80 degrees, preferably a range of 30 to 60 degrees, more preferably a range of 30 to 45 degrees, and is 30 degrees in the embodiment.
  • the efficiency of heat exchange between the exhaust gas and the heat exchange medium can be enhanced.
  • the wavelike depression-and-projection portions 33 , 34 make the condensed water adhered thereto by the flow of the exhaust gas and the effect of the surface tension be collected in the depression portions 33 , and further guided to the respective vertically lower portions, enabling the condensed water discharge performance.
  • the shell 40 is formed as a case having a substantial rectangular parallelepiped shape that houses the plurality of heat-exchange tubes 30 connected via the connecting pipes 31 a , 32 a , using a plate material having a thickness of 0.3 mm and including a metal material having an excellent acid corrosion resistance (for example, stainless steel) as with the respective heat-exchange tubes 30 , and forms flow paths 46 a , 46 b , 46 c , 46 d for exhaust gas jointly with the plurality of heat-exchange tubes 30 .
  • an inlet 41 for exhaust gas is formed, and on the right side in FIG. 1 of a vertically lower portion of the shell 40 , an outlet for the exhaust gas is formed.
  • exhaust gas flows in from the inlet 41 formed at the vertically upper portion of the shell 40 , passes through the spaces between the plurality of heat-exchange tubes 30 and the flow paths 46 a , 46 b , 46 c , 46 d while meandering, and flows out from the outlet 42 formed at the vertically lower portion of the shell 40 . Accordingly, the exhaust gas and the heat exchange medium flowing in the plurality of heat-exchange tubes 30 have flows opposed to each other as a whole, enabling enhancement of the heat exchange efficiency.
  • a plurality of heat-exchange tubes 30 are arranged in parallel at an interval of 1.6 mm in such a manner that each of the respective longitudinal directions thereof is a vertical direction, the heat exchange medium is made to flow in from the respective inlets 31 positioned at the vertically lower portions, flow in the respective heat-exchange tubes 30 toward the vertically upper portions, and flow out from the respective outlets 32 positioned at the vertically upper portions of the respective heat-exchange tubes 30 .
  • the exhaust gas is made to flow in from the inlet 41 formed at the vertically upper portion of the shell 40 , flow in the flow paths 46 a , 46 b , 46 c , 46 d formed by the shell 40 , the plurality of heat-exchange tubes 30 and the guide walls 43 , 44 and the spaces between the plurality of heat-exchange tubes 30 while meandering, and flow out from the outlet 42 formed at the vertically lower portion of the shell 40 , whereby the exhaust gas and the heat-exchange medium flowing in the plurality of heat-exchange tubes 30 have flows opposed to each other as a whole, enabling enhancement of the heat exchange efficiency.
  • the heat exchanger 20 as a result of forming the vertical groove 36 at a center of each of the flat surfaces of the heat-exchange tubes 30 , condensed water generated on the flat surfaces of the heat-exchange tubes 30 as a result of heat exchange with the exhaust gas can be collected and guided to the vertically lower portions, enabling enhancement of the condensed water discharge performance, and the strength of the plurality of heat-exchange tubes 30 can be enhanced, and the plurality of heat-exchange tubes 30 can be formed using a metal material having a small thickness, whereby a heat exchanger having a smaller size can be provided.
  • the grooves are fixed by bonding inside the respective tubes, enabling enhancement of the strength of the heat-exchange tubes 30 .
  • the wavelike depression-and-projection portions 33 , 34 including the depression portions 33 and the projection portions 34 flexed at the predetermined angle ⁇ relative to a horizontal direction in which the exhaust gas mainly flow to be continuous with one another, a secondary flow of the exhaust gas can be made to occur in addition to the main flow thereof, and consequently, the efficiency of heat exchange between the exhaust gas and the heat exchange medium can be enhanced.
  • the wavelike depression-and-projection portions 33 , 34 collect condensed water adhered thereto by the flow of the exhaust gas into the depression portions 33 and guide the condensed water to the vertically lower portions, enabling further enhancement of the condensed water discharge performance.
  • the heat exchanger 20 includes the groove 36 formed at the center of each of the flat surfaces of the plurality of heat-exchange tubes 30 and the wavelike depression-and-projection portions 33 , 34 formed over the substantial entirety of the flat surface, as in a heat exchanger 20 B according to an alteration in FIG. 5 , it is possible that a groove 36 is formed at a center of each of flat surfaces of a plurality of heat-exchange tubes 30 B but no wavelike depression-and-projection portions 33 , 34 are formed at the flat surface, and conversely, as in a heat exchanger 20 C according to an alteration in FIG.
  • the heat exchanger 20 includes the groove 36 formed at the center of each of the flat surfaces of the plurality of heat-exchange tubes 30 and the wavelike depression-and-projection portions 33 , 34 formed over the substantial entirety of the flat surface, as in a heat exchanger 20 D according to an alteration in FIG. 7 , ribs 37 a to 37 d , which project outward, may be formed at positions in each of flat surfaces of a plurality of heat-exchange tubes 30 D, the positions being aligned with guide walls 43 , 44 . Consequently, meandering of exhaust gas can be guided more reliably.
  • the adjacent ribs 37 a and rib 37 b , and the adjacent ribs 37 c and rib 37 d are preferably separated, respectively, by a groove 36 .
  • ribs are formed at positions at the flat surface of the plurality of heat-exchange tubes 30 D, the positions being aligned with the guide walls 43 , 44 , as in a heat exchanger 20 E according to an alteration in FIG. 8 , only ribs 37 a , 37 d extending from respective parts of each of the flat surfaces of the plurality of heat-exchange tubes 30 E, the parts being adjacent to the guide walls 43 , 44 , to the groove 36 may be formed.
  • the angle ⁇ of the wavelike depression-and-projection portions 33 , 34 formed at the flat surfaces relative to the horizontal direction is 30 degrees, the angle ⁇ only needs to fall within a range of 10 to 80 degrees, preferably a range of 30 to 60 degrees. Also, as in a heat-exchange tube 30 F according to an alteration in FIG.
  • an angle ⁇ of wavelike depression-and-projection portions 33 Fa, 34 Fa positioned on the exhaust gas inflow side relative to the horizontal direction is small, and an angle ⁇ of wavelike depression-and-projection portions 33 Fb, 34 Fb positioned in the exhaust gas outflow side relative to the horizontal direction is larger than the angle ⁇ .
  • the angle ⁇ is preferably 10 to 45 degrees and the angle ⁇ is preferably 45 to 80 degrees.
  • the heat-exchange tube 30 F according to the alteration, an angle of 30 degrees is employed for the angle ⁇ and an angle of 60 degrees is employed for the angle ⁇ .
  • wavelike depression-and-projection portions 33 , 34 may be formed in such a manner that the angles of the wavelike depression-and-projection portions 33 , 34 relative to the horizontal direction are larger from the exhaust gas inflow side toward the exhaust gas outflow side successively or stepwise.
  • the plurality of heat-exchange tubes 30 are formed so as to be a flat pipe, using a plate material having a thickness of 0.3 mm and including stainless steel, the flat pipe having a substantially rectangular shape in its entirety, which has a height (length) of 150 mm, a width of 30 mm and an inner heat exchange medium flow path thickness of 2.4 mm (an entire thickness of 3.0 mm including the thickness of the plate), and are arranged in parallel so as to provide a space of 1.6 mm between respective adjacent heat-exchange tubes 30 in such a manner that each of the longitudinal directions thereof is the vertical direction, any plate material may be employed as long as such plate material is one including a metal material having an excellent acid corrosion resistance other than stainless steel, and the thickness of the plate material may be smaller or larger than 0.3 mm if the strength can be maintained.
  • each of the plurality of heat-exchange tubes 30 have a shape of a substantially-rectangular flat hollow pipe, and the shape may be, for example, an oval flat hollow pipe.
  • the interval of adjacent heat-exchange tubes 30 is not limited to 1.6 mm, and an interval with any size may be employed as long as such interval is no more than 3 mm.
  • the plurality of heat-exchange tubes 30 be arranged in parallel in such a manner that each of the respective longitudinal directions thereof is exactly the vertical direction, and the plurality of heat-exchange tubes 30 may be arranged in parallel in such a manner that each of the respective longitudinal directions thereof is the vertical direction when a certain degree is added thereto.
  • the shell 40 is formed as a case having a substantially-rectangular parallelepiped shape that houses the plurality of heat-exchange tubes 30 using a plate material having a thickness of 0.3 mm and including stainless steel, any plate material having an excellent acid corrosion resistance other than stainless steel may be employed, and the thickness of the plate material may be smaller or larger than 0.3 mm if the strength can be maintained.
  • the shell 40 is formed as a case having a substantially-rectangular parallelepiped shape that houses the plurality of heat-exchange tubes 30 , and the guide walls 43 , 44 are provided inside the shell 40 so that exhaust gas flows in the spaces between the plurality of heat-exchange tubes 30 and the flow paths 46 a , 46 b , 46 c , 46 d while meandering, as in a heat exchanger 20 G according to an alteration in FIG.
  • the plurality of ribs 37 a to 37 d formed on the flat surfaces of the plurality of heat-exchange tubes 30 D and the shell 40 G can make exhaust gas flow in spaces between the plurality of heat-exchange tubes 30 D while meandering without forming guide walls inside the shell 40 G, enabling enhancement of the heat exchange efficiency.
  • the present invention is preferably applied to the manufacturing industries of heat exchangers.
US13/575,727 2010-02-02 2011-01-27 Heat exchanger Abandoned US20130032320A1 (en)

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JP2010021027A JP5620685B2 (ja) 2010-02-02 2010-02-02 熱交換器
JP2010-021027 2010-02-02
PCT/JP2011/051617 WO2011096324A1 (ja) 2010-02-02 2011-01-27 熱交換器

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CN (1) CN102822617B (zh)
WO (1) WO2011096324A1 (zh)

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JP2014222115A (ja) * 2013-05-13 2014-11-27 三菱電機ビルテクノサービス株式会社 熱交換器
JP2015207535A (ja) * 2014-04-23 2015-11-19 京セラ株式会社 燃料電池装置
US10648742B2 (en) 2016-03-16 2020-05-12 Mitsubishi Electric Corporation Finless heat exchanger, outdoor unit of an air-conditioning apparatus including the finless heat exchanger, and indoor unit of an air-conditioning apparatus including the finless heat exchanger
US10962308B2 (en) * 2016-08-30 2021-03-30 Alfa Laval Corporate Ab Plate heat exchanger for solar heating
CN112648874A (zh) * 2020-12-26 2021-04-13 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

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JP6459027B2 (ja) * 2014-07-15 2019-01-30 国立大学法人 東京大学 熱交換器
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CN105674789B (zh) * 2016-01-19 2018-01-19 昆明五威科工贸有限公司 一种水箱
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