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WO2018145674A1 - An annular heat exchanger - Google Patents

An annular heat exchanger Download PDF

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Publication number
WO2018145674A1
WO2018145674A1 PCT/CZ2018/000008 CZ2018000008W WO2018145674A1 WO 2018145674 A1 WO2018145674 A1 WO 2018145674A1 CZ 2018000008 W CZ2018000008 W CZ 2018000008W WO 2018145674 A1 WO2018145674 A1 WO 2018145674A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
thermal conductive
conductive structure
heat exchanger
exchanger
Prior art date
Application number
PCT/CZ2018/000008
Other languages
French (fr)
Inventor
Pavel SUMERA
Original Assignee
SUAR.CZ s.r.o.
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 SUAR.CZ s.r.o. filed Critical SUAR.CZ s.r.o.
Priority to EP18708568.3A priority Critical patent/EP3580514B1/en
Priority to UAA201907579A priority patent/UA124277C2/en
Priority to KR1020197021799A priority patent/KR20190116277A/en
Priority to CA3049295A priority patent/CA3049295C/en
Priority to US16/482,670 priority patent/US20190353428A1/en
Priority to DK18708568.3T priority patent/DK3580514T3/en
Priority to BR112019012305A priority patent/BR112019012305A2/en
Priority to PL18708568T priority patent/PL3580514T3/en
Priority to JP2019564575A priority patent/JP2020507740A/en
Priority to RU2019122167A priority patent/RU2019122167A/en
Priority to ES18708568T priority patent/ES2841826T3/en
Priority to CN201880008242.1A priority patent/CN110214256A/en
Publication of WO2018145674A1 publication Critical patent/WO2018145674A1/en

Links

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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/103—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 one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element

Definitions

  • a tube for exchangers, filled with a heat-exchange surface having the shape of fins is known from the patent US6533030. Further, heat exchangers are known that are filled with a honeycomb-shaped structure.
  • the Japanese patents JPH02150691 and JPS62288495 can be mentioned as an example.
  • the object of the invention is to adapt known "tube-in-tube” exchangers to achieve a considerable weight reduction and an increase of the exchanger output.
  • the tube profiles do not primarily form a heat exchange surface, but a piece of the exchanger that separates the media so the tube profiles can be sized to the respective pressure difference and the exchanger according to the invention can be used for almost any media pressure difference. Since the thermal conductive structure can have a thickness of tens of micrometers regardless of the media pressures while the thickness of the wall and possible fins in finned tubes of known exchangers is on the orders of millimeters, i.e. 2 orders thicker, the weight of the exchanger according to the invention is considerably lower at the same output.
  • the tube profiles can have in principle any cross-section, especially circular, oval, or rectangular.
  • the thermal conductive structure preferably fills the tube profiles completely.
  • FIG. 1 schematically shows a cross-section of the first example of an annular heat exchanger according to the invention.
  • Fig. 2 shows a detail of the design of the thermal conductive structure in the area of the inner profile.
  • Figs. 3, 4, 5 and 6 show other embodiments of annular heat exchanger according to the invention.
  • An embodiment of an annular heat exchanger according to Fig. 1 comprises three concentrically arranged tube profiles for media flow, namely the outer profile 1, inner profile 2 and central profile 7.
  • the tube profiles 1 , 2, 7 consist of tubes with a circular cross-section
  • the intermediate spaces between these profiles 1 , 2, 7 are completely filled with a thermal conductive structure 3 that is composed of a helically tightly wound pair of bands 4, 5 of aluminum sheet with the thickness of 0,05mm, lying on each other.
  • the first band 4 is smooth while the other band 5 is corrugated transversally to the winding direction to produce flow channels 6 (see Fig. 2).
  • the embodiment of an annular heat exchanger according to Fig. 3 only differs from the embodiment of Fig. 1 in that it does not have a central profile 7 and that the entire inner profile 2 is completely filled by the thermal conductive structure 3.
  • Figs. 5 and 6 show examples of exchangers whose tube profiles 1 , 2 have a rectangular cross-section. A skilled person will find it obvious that the profiles 1 , 2, 7 can virtually have any cross-section with enclosed circumference.
  • the annular heat exchanger according to the present invention can be connected as a counter-current or co-current exchanger with any number of inserted profiles 1 , 2, 7.
  • the exchanger can also be used for liquid/liquid media, but its benefits are maximally manifested when used for gas/gas and gas/liquid media and in applications with a high pressure difference at the hot and cold side (steam generators, recuperators of combustion turbines, condensers, evaporators).
  • Hot medium is supplied to the space between the inner profile 2 and the central profile 7 where the medium transfers heat by convection into the thermal conductive structure 3.
  • the thermal conductive structure 3 conducts this heat to the tube that forms the inner profile 2 and subsequently the heat is conducted to the thermal conductive structure 3 that fills the space between the inner profile 2 and the outer profile 1. In this space, the thermal conductive structure 3 transfers heat by convection into the colder medium that flows in this space. The motion of heat is indicated with arrows in Fig. 2.
  • the annular heat exchanger according to the present invention is based on 5 combined heat exchange when thermal convection has the same importance as thermal conduction. Its heat transfer surface is maximized by insertion of the thermal conductive structure 3 described above. Heat transfer into this thermal conductive structure 3 and the subsequent thermal conduction by this thermal conductive structure 3 to the separating wall of the respective profile 1 , 2, 7 are l o equally used for the heat exchange. Thus, thermal conduction by the thermal conductive structure 3 is applied to a considerably higher extent, being equally important as thermal convection in the exchanger based on the present invention.
  • Individual thermal conductive structures 3 are separated from each other by the 15 respective tube profiles 1 , 2, 7, which work as a heat exchange surface in standard exchangers, but in the inventive exchanger they predominantly act as media separators.
  • the exchanger based on the present invention can be used for virtually any pressure difference of media.
  • the tube profiles 1 , 2, 7 do not primarily form a heat-exchange surface, but a media-separating part of the exchanger. Since the thermal conductive structure can have a thickness of tens of micrometers regardless of the media pressures while the thickness of the 25 wall and possible fins in finned tubes of known exchangers is on the orders of millimeters, i.e. 2 orders thicker, the weight of the exchanger according to the invention is considerably lower at the same output.
  • a comparison calculation utilizing a numerical model in the ANSYS CFD program 30 was used to compare the heat output transferred by a 50-mm aluminum tube with the diameter of 20 mm in four versions, simulating 4 different types of exchangers:

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

An annular heat exchanger comprising at least two circumferentially enclosed tube profiles (1, 2) arranged inside each other for media flow and having a thermal conductive structure (3) arranged inside. The thermal conductive structure (3) comprises a helically tightly wound pair of bands (4, 5) lying on each other, the first band (4) being smooth, the other band (5) being corrugated transversally to the winding direction to create flow channels (6).

Description

An annular heat exchanger Technical Field The invention relates to an annular heat exchanger comprising at least two circumferentially enclosed tube profiles arranged inside each other for media flow and having a thermal conductive structure arranged inside.
Prior Art
Heat exchangers comprised of at least two tubes for media flow arranged inside each other are sometimes referred to as "tube-in-tube" exchangers. The tube in "tube-in-tube" exchangers has two principal functions - it separates the media and at the same time serves as a heat-exchange surface. Thermal convection from the media to the heat exchanger material is decisive for the exchange of heat, while thermal conduction is present to a minimal extent, just by the tube wall.
Increasing the heat exchange surface increases the output of the heat exchanger. In the "tube-in-tube" exchanger the tube length needs to be increased to increase the heat-exchange surface. As the tube separates the media at the same time, the entire heat exchange surface must have such a wall thickness to withstand the pressures of the media and their pressure difference. This makes the weight and size of such exchangers very large. The heat exchange surface can be increased by finning. The fins are part of the tube and have a thickness on the order of mm. In this case, both thermal convection and thermal conduction are partly present, but thermal convection is still decisive. Finning (increasing of the heat exchange surface) is used unilaterally - inside or outside.
To achieve maximum output with a minimum exchanger weight, there is an effort to reduce the thickness of the wall separating the media, which is restricted by technological limits especially if media having high or different pressures are concerned. In addition, these thin walls need to be joined in a way - e.g. by soldering or welding in the case of plate exchangers. This has certain technological limits as well.
A tube for exchangers, filled with a heat-exchange surface having the shape of fins is known from the patent US6533030. Further, heat exchangers are known that are filled with a honeycomb-shaped structure. The Japanese patents JPH02150691 and JPS62288495 can be mentioned as an example.
Further, rotary regenerative heat exchangers made e.g. by the company KASST are known, which use the condenser principle, which means that they are cyclically charged and after the charged part of the heat exchange surface is turned to a place with a lower temperature they are discharged again. This is quite a different functional principle from that of "tube-in-tube" exchangers from the technical point of view.
The object of the invention is to adapt known "tube-in-tube" exchangers to achieve a considerable weight reduction and an increase of the exchanger output.
Disclosure of Invention
The said object is achieved through an annular heat exchanger comprising at least two circumferentially enclosed tube profiles arranged inside each other for media flow and having a thermal conductive structure arranged inside according to the invention, the principle of which is that the thermal conductive structure comprises a helically tightly wound pair of bands lying on each other, the first band being smooth, the other band being corrugated transversally to the winding direction to create flow channels. An advantage of the invention is that the individual thermal conductive structures are separated from each other by the respective tube profiles which work as a heat exchange surface in standard exchangers, but in the inventive exchanger they predominantly act as media separators. The tube profiles do not primarily form a heat exchange surface, but a piece of the exchanger that separates the media so the tube profiles can be sized to the respective pressure difference and the exchanger according to the invention can be used for almost any media pressure difference. Since the thermal conductive structure can have a thickness of tens of micrometers regardless of the media pressures while the thickness of the wall and possible fins in finned tubes of known exchangers is on the orders of millimeters, i.e. 2 orders thicker, the weight of the exchanger according to the invention is considerably lower at the same output.
The tube profiles can have in principle any cross-section, especially circular, oval, or rectangular.
The thermal conductive structure preferably fills the tube profiles completely.
Brief Description of Drawings
Fig. 1 schematically shows a cross-section of the first example of an annular heat exchanger according to the invention. Fig. 2 shows a detail of the design of the thermal conductive structure in the area of the inner profile. Figs. 3, 4, 5 and 6 show other embodiments of annular heat exchanger according to the invention.
Description of preferred embodiments
An embodiment of an annular heat exchanger according to Fig. 1 comprises three concentrically arranged tube profiles for media flow, namely the outer profile 1, inner profile 2 and central profile 7. In this embodiment, the tube profiles 1 , 2, 7 consist of tubes with a circular cross-section The intermediate spaces between these profiles 1 , 2, 7 are completely filled with a thermal conductive structure 3 that is composed of a helically tightly wound pair of bands 4, 5 of aluminum sheet with the thickness of 0,05mm, lying on each other. The first band 4 is smooth while the other band 5 is corrugated transversally to the winding direction to produce flow channels 6 (see Fig. 2). The embodiment of an annular heat exchanger according to Fig. 3 only differs from the embodiment of Fig. 1 in that it does not have a central profile 7 and that the entire inner profile 2 is completely filled by the thermal conductive structure 3.
The embodiment of an annular heat exchanger in accordance to Fig. 4 comprises several central profiles 7. In such a case, there may be two media, or the exchanger can be designed for heat exchange between more media.
Figs. 5 and 6 show examples of exchangers whose tube profiles 1 , 2 have a rectangular cross-section. A skilled person will find it obvious that the profiles 1 , 2, 7 can virtually have any cross-section with enclosed circumference.
The annular heat exchanger according to the present invention can be connected as a counter-current or co-current exchanger with any number of inserted profiles 1 , 2, 7. The exchanger can also be used for liquid/liquid media, but its benefits are maximally manifested when used for gas/gas and gas/liquid media and in applications with a high pressure difference at the hot and cold side (steam generators, recuperators of combustion turbines, condensers, evaporators).
The function of an annular heat exchanger according to the present invention will be described using the embodiment shown in Fig. 1 and 2. The other embodiments work in an analogous way.
Hot medium is supplied to the space between the inner profile 2 and the central profile 7 where the medium transfers heat by convection into the thermal conductive structure 3. The thermal conductive structure 3 conducts this heat to the tube that forms the inner profile 2 and subsequently the heat is conducted to the thermal conductive structure 3 that fills the space between the inner profile 2 and the outer profile 1. In this space, the thermal conductive structure 3 transfers heat by convection into the colder medium that flows in this space. The motion of heat is indicated with arrows in Fig. 2.
Thus, the annular heat exchanger according to the present invention is based on 5 combined heat exchange when thermal convection has the same importance as thermal conduction. Its heat transfer surface is maximized by insertion of the thermal conductive structure 3 described above. Heat transfer into this thermal conductive structure 3 and the subsequent thermal conduction by this thermal conductive structure 3 to the separating wall of the respective profile 1 , 2, 7 are l o equally used for the heat exchange. Thus, thermal conduction by the thermal conductive structure 3 is applied to a considerably higher extent, being equally important as thermal convection in the exchanger based on the present invention.
Individual thermal conductive structures 3 are separated from each other by the 15 respective tube profiles 1 , 2, 7, which work as a heat exchange surface in standard exchangers, but in the inventive exchanger they predominantly act as media separators.
As the media are separated by the tube profiles 1 , 2, 7 that are designed for the 20 respective pressure difference, the exchanger based on the present invention can be used for virtually any pressure difference of media. Thus, the tube profiles 1 , 2, 7 do not primarily form a heat-exchange surface, but a media-separating part of the exchanger. Since the thermal conductive structure can have a thickness of tens of micrometers regardless of the media pressures while the thickness of the 25 wall and possible fins in finned tubes of known exchangers is on the orders of millimeters, i.e. 2 orders thicker, the weight of the exchanger according to the invention is considerably lower at the same output.
A comparison calculation utilizing a numerical model in the ANSYS CFD program 30 was used to compare the heat output transferred by a 50-mm aluminum tube with the diameter of 20 mm in four versions, simulating 4 different types of exchangers:
- smooth tube
- standard finned tube - finned tube according to the patent US6533030
- exchanger in accordance with the invention
Calculation conditions: a tube heated from the outside to the constant temperature of 100°C; air entering the tube having the temperature of 20°C and flow speed of 31.87 m/s.
An ideal exchanger having 100 % efficiency would have the output of 604 W. Using the numerical model, the following values were calculated:
Smooth tube - 32 W (5 % of the ideal exchanger)
Standard finned tube - 146 W (24 % of the ideal exchanger)
Finned tube according to the patent US6533030 - 252 W (42 % of the ideal exchanger)
Exchanger in accordance with the invention - 375 W (62 % of the ideal exchanger)
From the above it is obvious that the inventive exchanger has by far the highest output.
List of reference signs:
1 outer profile
2 inner profile
3 thermal conductive structure
4 first band
5 second band
6 flow channel
7 central profile

Claims

1. An annular heat exchanger comprising of at least two circumferentially enclosed tube profiles (1 , 2) arranged inside each other for media flow and having a thermal conductive structure (3) arranged inside, characterized in that the thermal conductive structure (3) comprises a helically tightly wound pair of bands (4, 5) lying on each other, the first band (4) being smooth, the other band (5) being corrugated transversally to the winding direction to create flow channels (6). 2. The annular heat exchanger according to claim 1 , characterized in that the tube profiles (1 ,
2) have a circular, oval or rectangular cross-section.
3. The annular heat exchanger according to claim 1 or 2, characterized in that the thermal conductive structure (3) completely fills the tube profiles (1 , 2).
PCT/CZ2018/000008 2017-02-09 2018-02-05 An annular heat exchanger WO2018145674A1 (en)

Priority Applications (12)

Application Number Priority Date Filing Date Title
EP18708568.3A EP3580514B1 (en) 2017-02-09 2018-02-05 An annular heat exchanger
UAA201907579A UA124277C2 (en) 2017-02-09 2018-02-05 An annular heat exchanger
KR1020197021799A KR20190116277A (en) 2017-02-09 2018-02-05 Annular heat exchanger
CA3049295A CA3049295C (en) 2017-02-09 2018-02-05 An annular heat exchanger
US16/482,670 US20190353428A1 (en) 2017-02-09 2018-02-05 Annular heat exchanger
DK18708568.3T DK3580514T3 (en) 2017-02-09 2018-02-05 Annular heat exchanger
BR112019012305A BR112019012305A2 (en) 2017-02-09 2018-02-05 annular heat exchanger.
PL18708568T PL3580514T3 (en) 2017-02-09 2018-02-05 An annular heat exchanger
JP2019564575A JP2020507740A (en) 2017-02-09 2018-02-05 Annular heat exchanger
RU2019122167A RU2019122167A (en) 2017-02-09 2018-02-05 RING HEAT EXCHANGER
ES18708568T ES2841826T3 (en) 2017-02-09 2018-02-05 Annular heat exchanger
CN201880008242.1A CN110214256A (en) 2017-02-09 2018-02-05 Circular heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CZPV2017-77 2017-02-09
CZ2017-77A CZ201777A3 (en) 2017-02-09 2017-02-09 An annular heat exchanger

Publications (1)

Publication Number Publication Date
WO2018145674A1 true WO2018145674A1 (en) 2018-08-16

Family

ID=69738387

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CZ2018/000008 WO2018145674A1 (en) 2017-02-09 2018-02-05 An annular heat exchanger

Country Status (14)

Country Link
US (1) US20190353428A1 (en)
EP (1) EP3580514B1 (en)
JP (1) JP2020507740A (en)
KR (1) KR20190116277A (en)
CN (1) CN110214256A (en)
BR (1) BR112019012305A2 (en)
CA (1) CA3049295C (en)
CZ (1) CZ201777A3 (en)
DK (1) DK3580514T3 (en)
ES (1) ES2841826T3 (en)
PL (1) PL3580514T3 (en)
RU (1) RU2019122167A (en)
UA (1) UA124277C2 (en)
WO (1) WO2018145674A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115285939B (en) * 2022-08-24 2023-08-22 北京石油化工学院 A bioethanol autothermal reforming hydrogen production system

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US2589262A (en) * 1946-06-12 1952-03-18 Hydrocarbon Research Inc Heat exchanger
JPS62288495A (en) 1986-06-03 1987-12-15 Sumitomo Metal Ind Ltd Heat exchanger
JPH02150691A (en) 1988-11-30 1990-06-08 Kyocera Corp Honeycomb heat exchanger and its manufacturing method
JPH04335993A (en) * 1991-05-10 1992-11-24 Toyo Radiator Co Ltd Oil cooler
US6533030B2 (en) 2000-08-03 2003-03-18 F.W. Brokelmann Aluminiumwerk Gmbh & Co. Kg Heat transfer pipe with spiral internal ribs
JP2003307396A (en) * 2002-04-16 2003-10-31 Usui Kokusai Sangyo Kaisha Ltd Fin tube
WO2005050117A1 (en) * 2003-11-21 2005-06-02 Dana Canada Corporation Tubular charge air cooler

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JPS51116445A (en) * 1975-04-04 1976-10-13 Daikin Ind Ltd A dual-tube type heat exchanger and manufacturing process thereof
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JPS57165973U (en) * 1981-04-04 1982-10-19
DE3331186A1 (en) * 1983-08-30 1985-03-14 Spiro Research B.V., Helmond HEATING PIPE WITH ANGULAR WIRING PROFILE
US20060081362A1 (en) * 2004-10-19 2006-04-20 Homayoun Sanatgar Finned tubular heat exchanger
FR2887020B1 (en) * 2005-06-09 2007-08-31 Air Liquide PLATE HEAT EXCHANGER WITH EXCHANGE STRUCTURE FORMING MULTIPLE CHANNELS IN A PASSAGE
CN100516756C (en) * 2006-09-18 2009-07-22 西安交通大学 A casing metal foam heat exchanger
CN101334248B (en) * 2008-07-15 2011-06-01 西安石油大学 Longitudinal spiral inner finned tube
CN201392115Y (en) * 2009-03-17 2010-01-27 铜联商务咨询（上海）有限公司 A sleeve-type high-efficiency foam metal heat exchanger
CN104930878A (en) * 2015-05-20 2015-09-23 苏州锦珂塑胶科技有限公司 Heat exchanger and heat energy recovery device

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2589262A (en) * 1946-06-12 1952-03-18 Hydrocarbon Research Inc Heat exchanger
JPS62288495A (en) 1986-06-03 1987-12-15 Sumitomo Metal Ind Ltd Heat exchanger
JPH02150691A (en) 1988-11-30 1990-06-08 Kyocera Corp Honeycomb heat exchanger and its manufacturing method
JPH04335993A (en) * 1991-05-10 1992-11-24 Toyo Radiator Co Ltd Oil cooler
US6533030B2 (en) 2000-08-03 2003-03-18 F.W. Brokelmann Aluminiumwerk Gmbh & Co. Kg Heat transfer pipe with spiral internal ribs
JP2003307396A (en) * 2002-04-16 2003-10-31 Usui Kokusai Sangyo Kaisha Ltd Fin tube
WO2005050117A1 (en) * 2003-11-21 2005-06-02 Dana Canada Corporation Tubular charge air cooler

Also Published As

Publication number Publication date
CA3049295A1 (en) 2018-08-16
CN110214256A (en) 2019-09-06
EP3580514A1 (en) 2019-12-18
BR112019012305A2 (en) 2019-11-12
EP3580514B1 (en) 2020-12-09
RU2019122167A (en) 2021-03-09
US20190353428A1 (en) 2019-11-21
UA124277C2 (en) 2021-08-18
DK3580514T3 (en) 2021-01-11
RU2019122167A3 (en) 2021-03-09
CZ307349B6 (en) 2018-06-20
JP2020507740A (en) 2020-03-12
CZ201777A3 (en) 2018-06-20
PL3580514T3 (en) 2021-06-14
CA3049295C (en) 2022-12-06
ES2841826T3 (en) 2021-07-09
KR20190116277A (en) 2019-10-14

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