WO2018158843A1 - 熱交換器 - Google Patents
熱交換器 Download PDFInfo
- Publication number
- WO2018158843A1 WO2018158843A1 PCT/JP2017/007912 JP2017007912W WO2018158843A1 WO 2018158843 A1 WO2018158843 A1 WO 2018158843A1 JP 2017007912 W JP2017007912 W JP 2017007912W WO 2018158843 A1 WO2018158843 A1 WO 2018158843A1
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- WO
- WIPO (PCT)
- Prior art keywords
- pipe
- heat exchanger
- coil
- annular flow
- tube
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D7/02—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 helically coiled
- F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D7/02—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 helically coiled
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0087—Fuel coolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M8/00—Fuel cells; Manufacture thereof
- H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
- H01M8/04298—Processes for controlling fuel cells or fuel cell systems
- H01M8/04694—Processes for controlling fuel cells or fuel cell systems characterised by variables to be controlled
- H01M8/04701—Temperature
- H01M8/04708—Temperature of fuel cell reactants
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/50—Fuel cells
Definitions
- the present invention relates mainly to a heat exchanger used for cooling, for example, a heat exchanger suitable for a precooler for precooling hydrogen gas supplied to a fuel cell vehicle to a desired temperature in a short time.
- a shell and coil type heat exchanger is widely known as a cooling heat exchanger.
- This shell-and-coil type heat exchanger uses a coiled tube having a helical flow path and a shell (container, cylinder, tube, etc.) covering the coiled tube, and coils one of two fluids having different thermal energy. It is made to flow into the pipe and flow or stagnate the other out of the same coil pipe to perform efficient heat exchange between the two fluids.
- each of the heat exchangers shown in Patent Documents 1 and 2 below has a double pipe structure consisting of an inner pipe and an outer pipe coaxially arranged, and between the outer peripheral surface of the inner pipe and the inner peripheral surface of the outer pipe
- a helical flow path is formed by the coil tube along the axial direction, and heat exchange is performed between the fluid flowing in the annular flow path and the fluid flowing in the helical flow path It has become.
- the axial direction of the heat exchanger is the vertical direction, and naturally the annular channel is a channel extending in the vertical direction. Then, it is premised that in any heat exchanger, the fluid existing in the annular flow channel flows downward (falls) by gravity and is accumulated at the bottom of the annular flow channel.
- the heat exchange with the fluid flowing in the spiral flow channel becomes unbalanced between the portion where the fluid existing in the annular flow channel is accumulated and the position where the fluid is flowing, and it is difficult to perform heat exchange with high efficiency. doing. In particular, it is unsuitable for heat exchange for the purpose of fluid cooling in a short time.
- the heat exchanger of Patent Document 1 uses the inside of the inner pipe as a supply conduit for guiding the fluid to the annular flow path, and the heat exchanger of Patent Document 2 applies the annular flow path of the inside of the inner pipe. Used as a discharge conduit to discharge fluid from the
- the heat exchangers of Patent Documents 1 and 2 described above are a fluid flowing inside the inner pipe and a fluid in the annular flow channel. Heat exchange with is also assumed. Therefore, it is inefficient as compared with the case where only heat exchange between the fluid in the annular channel and the fluid in the spiral channel is performed. Therefore, the heat exchange for the purpose of fluid cooling in a short time is also unsuitable.
- the present invention radically changes the structure of the conventional shell-and-coil type heat exchanger described above, and provides a heat exchanger having a dramatically improved efficiency of heat exchange although having a simple structure.
- the heat exchanger according to the present invention has a double pipe structure comprising an inner pipe and an outer pipe coaxially arranged, and is axially arranged between the outer peripheral surface of the inner pipe and the inner peripheral surface of the outer pipe.
- a flow passage is not formed inside the inner pipe. The heat exchange is performed between the cooling fluid flowing in the fixed direction in the annular flow passage and the fluid to be cooled flowing in the fixed direction in the spiral flow passage, thereby cooling the fluid to be cooled with high efficiency without unevenness. be able to.
- the direction in which the cooling fluid flows is countercurrent to the direction in which the cooling fluid flows, so that heat exchange can be performed more efficiently, and in a short period of time the cooling fluid can be cooled. Allow for cooling.
- the coil tube can be inserted into and removed from the annular flow passage, and maintenance such as inspection of the coil tube peripheral wall can be facilitated. Therefore, safety can be ensured even when the fluid to be cooled is a fluid that requires careful handling.
- the coil average of the coil tube such that the cross sectional area of the outer annular flow channel outside the coil pipe and the cross sectional area of the inner annular flow channel inside the coil pipe are the same.
- a proper shape of the cooling fluid and the fluid to be cooled is secured by providing the coiled tube with a shape retaining member that maintains the entire shape and coil pitch of the coiled tube along the axial direction.
- a heat insulating material is disposed only in one of the inside of the inner pipe or the outside of the outer pipe, or a heat insulating material is disposed both in the inner of the inner pipe and the outer of the outer pipe to further increase the heat exchange efficiency. You can do better.
- the heat exchanger according to the present invention can cool the fluid to be cooled reliably in a short time despite the simple structure. In addition, due to the simple structure, the material cost and the assembly cost can be suppressed.
- neither the cooling fluid nor the fluid to be cooled flows in a fixed direction, so that there is no loss in each flow energy. Therefore, a plurality of heat exchangers can be easily connected, and the heat exchange can be further efficient.
- a coiled tube can be inserted and removed between the inner and outer tubes, which is excellent in maintainability and safety.
- FIG. 6 is a cross-sectional view taken along the line XX in FIG.
- It is an expansion left side view of a heat exchanger concerning the present invention.
- It is an expansion left side view showing other examples of a heat exchanger concerning the present invention.
- It is a conceptual diagram which shows the example of connection of the heat exchanger which concerns on this invention.
- It is a conceptual diagram which shows the other connection example of the heat exchanger which concerns on this invention.
- a precooler for precooling hydrogen gas supplied to a fuel cell vehicle is mentioned as a heat exchanger, but the heat exchanger according to the present invention is a heat exchanger for cooling hydrogen gas.
- the heat exchanger according to the present invention is a heat exchanger for cooling hydrogen gas.
- it is not limited to
- the heat exchanger 1 according to the present invention has a double pipe structure including an inner pipe 2 coaxially disposed with the central axis O in common and an outer pipe 3.
- An annular flow passage 4 having an annular cross-sectional shape is formed along the axial direction between the outer circumferential surface 2 a of the outer circumferential surface 2 a and the inner circumferential surface 3 b of the armored tube 3.
- the axial direction of the heat exchanger 1 according to the present invention may be vertical or horizontal. That is, the heat exchanger 1 may be placed vertically or horizontally.
- the present embodiment will be described on the assumption of a precooler for hydrogen gas cooling. Therefore, the case where heat exchange is performed between brine (antifreeze liquid) which is a cooling fluid flowing in the annular flow channel 4 and hydrogen gas which is a to-be-cooled fluid flowing in the spiral flow channel 6 will be described. That is, the cooling fluid is a liquid, and the fluid to be cooled is a gas. Hydrogen gas, which is the fluid to be cooled, is cooled to about 40 ° C to -37 ° C.
- the brine is not particularly limited as long as it is liquid at around -40 ° C., which is the supply temperature, and, for example, hydrofluoroether (HFE), an aqueous solution of potassium formate and the like are used.
- HFE hydrofluoroether
- the inner pipe 2 is a circular pipe made of metal such as stainless steel, and has an inner diameter of 54.9 mm, an outer diameter of 60.5 mm, and a peripheral wall thickness of 2.8 mm. As shown in FIG. 4, the inner pipe 2 has an inner portion 2c surrounded by the inner circumferential surface 2b, but in the present invention, the inner portion 2c is not used as a flow path of brine or hydrogen gas. That is, the inside 2 c of the inner pipe 2 does not communicate with the annular channel 4 or the spiral channel 6.
- the inside 2 c is made hollow and functions as a heat insulating space, or a heat insulating material such as urethane foam is interposed.
- the heat exchange between the brine in the annular flow passage 4 and the hydrogen gas in the spiral flow passage 6 is specialized exclusively for realizing highly efficient heat exchange, This is to prevent unnecessary heat energy from being applied to the brine flowing in the flow path 4.
- a centering protrusion 2d is provided at one end in the axial direction of the inner tube 2, and the centering protrusion 2d is fitted with a receiving recess 3d provided in the one end tube 3A of the outer tube 3 described later.
- the inner pipe 2 and the outer pipe 3 can be properly coaxially arranged.
- the outer tube 3 is a circular tube made of metal such as stainless steel, and is composed of three divided tubes for ease of assembly and insertion and removal of the coil tube 5.
- the inner diameter is 108.3 mm
- the outer diameter is 114.3 mm
- the peripheral wall thickness is 3.0 mm with respect to the dimensions of the inner pipe 2 described above.
- the external tube 3 has one end tube 3A constituting one end in the axial direction, the central portion tube 3B constituting the central portion, and the other end constituting the other end in the axial direction
- Each of the pipes has a flange joint 7. Therefore, the outer tube 3 can be configured by firmly connecting the adjacent flange joints 7 of the adjacent pipes by fastening the adjacent pair of flange joints 7 with a plurality of bolts 8 and nuts 9. .
- a gasket is interposed between the pair of flange joints 7 which are butted to ensure sealing performance.
- the armoring tube 3 has a first supply conduit 10 for supplying brine to the annular channel 4 at one axial end, that is, the one-end pipe 3A.
- the other end in the axial direction that is, the other end 3C, has a first discharge conduit 11 for discharging brine from the annular flow passage 4.
- the first supply conduit 10 and the first discharge conduit 11 extend in a direction perpendicular to the axial direction of the armored tube 3 and in a tangential direction of the peripheral wall of the armored tube 3. Thereby, supply and discharge of brine to annular channel 4 can be made smooth.
- the first supply conduit 10 and the first discharge conduit 11 extending in the axial orthogonal direction from the both ends of the external tube 3 make one end of the axial line 4 of the annular flow passage 4 as shown in FIG. It flows from one end in the axial direction of the pipe 3 to the other end (the other end in the axial direction of the external pipe 3).
- the brine which is the cooling fluid, flows in a fixed direction in the annular flow path 4, that is, in the axial direction as indicated by the solid arrow in the figure.
- first supply conduit 10 and the first discharge conduit 11 extend on the same tangent with respect to the peripheral wall of the armored tube 3 and in the direction orthogonal to the axial direction of the armored tube 3.
- the supply and discharge of brine can be smoother.
- the first supply conduit 10 and the first discharge conduit 11 extend in the same direction in the direction orthogonal to the exterior tube 3 and on tangents respectively facing the peripheral wall of the exterior tube 3. It can be configured.
- the flow direction of the cooling fluid brine in the annular flow passage 4 can be three-dimensionally countercurrent to the flow direction of the coiled tube 5, that is, the flow direction of the hydrogen gas to be cooled fluid in the helical flow passage 6, Further, heat exchange can be performed more efficiently, which in turn enables hydrogen gas to be cooled in a short time.
- protective pipes 3c extending in the axial direction are provided, respectively.
- the coiled tube 5 is fixed while protecting the fifth supply conduit 13 and the second discharge conduit 14.
- a heat insulating material such as a special elastomer can be disposed so as to cover the outside of the exterior tube 3, that is, the outer peripheral surface 3a. This is to prevent unnecessary heat energy from being applied to the brine flowing in the annular flow passage 4.
- the coil tube 5 is, for example, an average diameter of a circular tube having an inner diameter of 4.93 mm, an outer diameter of 9.53 mm, and a peripheral wall thickness of 2.3 mm with respect to the dimensions of the inner tube 2 and outer tube 3 described above.
- the coil pitch is set to 16.18 mm at an average of 87.2 mm of the coil outer diameter and the coil inner diameter, and is spirally formed.
- a steel material such as austenitic stainless steel having a Ni equivalent value of 28.5% to 32.09% and a tensile strength of 800 N or more is desirable. This is because the peripheral wall thickness of the coil tube itself which is shaped (deformed) into a coil shape can be made as thin as possible, and the resistance to hydrogen gas is high.
- the coiled tube 5 is formed in the shape of a solenoid coil, that is, the coil average diameter is formed as a spiral having an equal diameter over the entire length.
- the coil mean diameter can be increased or decreased over a partial length, and the flow rate of the brine can be adjusted in cooperation with the annular channel 4.
- a second discharge conduit 14 for discharging hydrogen gas from the spiral flow passage 6 is provided at one end in the axial direction of the coil tube 5 and hydrogen gas as a fluid to be cooled is made to the spiral flow passage 6 at the other end.
- a second feed conduit 13 is provided for feeding.
- the second supply conduit 13 and the second discharge conduit 14 extend parallel to and in the direction opposite to the axial direction of the coiled tube 5.
- the second supply conduit 13 and the second discharge conduit 14 are disposed opposite to each other in the circumferential direction of the coil.
- the coiled tube 5 having the above-described configuration can be easily inserted in and removed from the annular flow passage 4 between the inner tube 2 and the outer tube 3. That is, as described above, the outer tube 3 can be divided into the one end tube 3A, the central portion tube 3B and the other end tube 3C, and the second discharge conduit 14 which is one end of the coil tube 5 is also the other end. This is because the second supply conduit 13 is only held by the protective pipe 3c of the external pipe 3 and no fixing means such as welding is required.
- the coiled tube 5 can be easily inserted into and removed from the annular flow passage 4, an inspection or the like on the peripheral wall of the coiled tube 5 can be easily performed, and maintenance becomes easy. Therefore, safety can be ensured even when using a fluid that is carefully handled, such as hydrogen gas.
- the coil tube 5 is provided with a shape-retaining material 12 for maintaining the overall shape and coil pitch of the coil tube 5 along the axial direction. To ensure proper flow of hydrogen gas flowing in the coil tube 5 and the coil tube 5.
- the shape retaining member 12 is composed of an outer shape retaining member 12A and an inner shape retaining member 12B, and the outer shape retaining member 12A and the inner shape retaining member 12B hold the coil tube 5 from inside and outside along the axial direction.
- the outer shape retaining member 12A and the inner shape retaining member 12B holding the coil tube 5 are bound with a stainless steel band or the like at an appropriate interval.
- the number of the shape retaining members 12 is not particularly limited.
- annular flow passage 4 is divided into an outer annular flow passage 4 A outside the coiled tube 5 and an inner annular flow passage 4 B inner than the coiled tube 5. Therefore, the brine is divided into the outer annular flow passage 4A and the inner annular flow passage 4B, and flows while sandwiching the coiled tube 5 and hence the spiral flow passage 6.
- the cross-sectional area of the outer annular flow path 4A ( ⁇ L3 2/2- ⁇ L2 2/2) cross-sectional area of the inner annular flow path 4B ( ⁇ L2 2/2- ⁇ L1 2/2
- L1 indicates the "outer diameter of the inner tube 2”
- L2 indicates the "coil average diameter”
- L3 indicates the "inner diameter of the outer tube 3".
- the brine is formed by narrowing the cross sectional areas of the annular flow channels 4A and 4B as much as possible while making the cross sectional area of the outer annular flow channel 4A equal to the cross sectional area of the inner annular flow channel 4B.
- High flow rate to achieve high efficiency heat exchange for example, in the case where the shape retaining member 12 is provided to the coil pipe 5 as described above, the shape retaining member 12 is sandwiched between the outer peripheral surface 2 a of the inner pipe 2 and the inner peripheral surface 3 b of the outer pipe 3.
- the cross-sectional area of the flow path 4A and the inner annular flow path 4B is made as narrow as possible.
- the thicknesses of the outer shape retaining member 12A and the inner shape retaining member 12B are adjusted so that the cross sectional area of the outer annular flow passage 4A and the cross sectional area of the inner annular flow passage 4B become equal.
- the coil average diameter L2 of the coiled tube 5 be four or more times the outer diameter L4 of the coiled tube 5.
- the coil pitch P is preferably 1.5 to 2.0 times the outer diameter L 4 of the coil tube 5. This is for the balance between the maintenance of the whole shape of the coiled tube 5 and the appropriate flow of the brine which is the cooling fluid flowing along the outer peripheral surface of the coiled tube 5.
- the annular flow path 4 and the spiral flow path 6 are configured, and hydrogen gas is flowed into the spiral flow path 6 while flowing brine from one end to the other end of the outer tube 3 in the axial direction through the annular flow path 4 It flows from the other end to the one end in the axial direction of the external tube 3 through the Therefore, in the heat exchanger 1 according to the present invention, the direction in which the brine or cooling fluid in the annular flow channel 4 flows and the direction in which the hydrogen gas or cooled fluid in the spiral flow channel 6 flows are three-dimensionally directed. It becomes a stream, can perform highly efficient heat exchange, and enables short-time cooling of hydrogen gas.
- the heat exchanger 1 according to the present invention can cool the fluid to be cooled reliably in a short time despite the simple structure.
- the material cost and the assembly cost can be suppressed.
- the heat exchanger since both the cooling fluid and the fluid to be cooled flow in a fixed direction, there is no loss in the flow energy of each fluid. Therefore, a plurality of heat exchangers can be easily connected, and the heat exchange can be further efficient.
- the two heat exchangers 1 can be connected in parallel, and the brine F1 and the hydrogen gas F2 can be separated and flowed in parallel to achieve further efficiency improvement.
- a pair of heat exchangers 1 connected in series are further arranged in parallel, and brine F1 and hydrogen gas F2 are respectively divided and flowed in parallel to the heat exchangers 1 of each pair. Further efficiency can be achieved.
- the number of heat exchangers 1 in parallel and the number of heat exchangers 1 in series can be adjusted appropriately.
- the heat exchanger 1 according to the present invention can easily insert and remove the coil pipe 5 between the inner pipe 2 and the outer pipe 3 and is excellent in maintainability and safety.
- the heat exchanger 1 according to the present invention can perform high-efficiency heat exchange while achieving cost reduction with a simple structure. In addition, it is excellent in maintainability and safety. Therefore, it is very convenient to use the heat exchanger 1 according to the present invention as a precooler installed at a hydrogen station, which can greatly contribute to the spread of fuel cell vehicles.
- SYMBOLS 1 Heat exchanger, 2 ... Interior pipe, 2a ... Outer peripheral surface, 2b ... Inner peripheral surface, 2c ... Inside, 2d ... Centering protrusion, 3 ... Outer tube, 3A ... One end part pipe, 3B ... Central part pipe, 3C ... Other end part pipe, 3a ... outer peripheral surface, 3b ... inner peripheral surface, 3c ... protection pipe, 3d ... centering projection receiving recess, 4 ... annular channel, 4A ... outer annular channel, 4B ... inner annular channel, DESCRIPTION OF SYMBOLS 5 ... Coil pipe, 6 ... Helical flow path, 7 ... Flange joint, 8 ... Bolt, 9 ...
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- Engineering & Computer Science (AREA)
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- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
図1乃至図4に示すように、本発明に係る熱交換器1は、中心軸Oを共通として同軸配置した内装管2と外装管3とから成る二重管構造を有し、内装管2の外周面2aと外装管3の内周面3b間に軸方向に沿って横断面形状が環状の環状流路4を形成すると共に、該環状流路4内に軸方向に沿ってコイル管5を配して螺旋状流路6を形成する基本構成を有している。本発明に係る熱交換器1の軸方向は上下方向でも左右方向でも良い。すなわち熱交換器1を縦置きしても横置きしても良い。
内装管2はステンレス等の金属から成る円管であり、例えば内径が54.9mm、外径が60.5mm、周壁厚が2.8mmである。該内装管2は、図4に示すように、内周面2bに囲まれた内部2cを有しているが、本発明において、この内部2cはブラインや水素ガスの流路としては用いない。つまり内装管2の内部2cは環状流路4にも螺旋状流路6にも通じていない。
外装管3はステンレス等の金属から成る円管であり、組立容易性及びコイル管5の挿抜のために、三つの分割された管から構成される。既述の内装管2の寸法例示に対して、例えば内径が108.3mm、外径が114.3mm、周壁厚が3.0mmに設定する。
コイル管5は、既述の内装管2及び外装管3の寸法例示に対して、例えば内径が4.93mm、外径が9.53mm、周壁厚が2.3mmの円管をコイル平均径(コイル外径とコイル内径との平均)87.2mmでコイルピッチ16.18mmとなるように設定し、螺旋状に巻いて形成する。該コイル管5の構成材としては、例えばオーステナイト系ステンレス鋼等のNi当量値が28.5%~32.09%で引張強度が800N以上の鋼材が望ましい。コイル状に成形(変形)されるコイル管自体の周壁厚を可及的に薄くできると共に、水素ガスに対して耐性が高いためである。
図4乃至図6に示すように、環状流路4はコイル管5よりも外側の外側環状流路4Aと、コイル管5よりも内側の内側環状流路4Bとに分かれる。よってブラインは外側環状流路4A内と内側環状流路4B内へと分流し、コイル管5、ひいては螺旋状流路6を挟みつつ流れることとなる。
Claims (7)
- 同軸配置した内装管と外装管から成る二重管構造を有し、該内装管の外周面と該外装管の内周面間に軸方向に沿って環状流路を形成すると共に、該環状流路内に軸方向に沿ってコイル管を配して螺旋状流路を形成する傍ら、上記内装管の内部には流路を形成しない構成を具備し、上記環状流路内を一定方向に流れる冷却流体と上記螺旋状流路内を一定方向に流れる被冷却流体間で熱交換を行うことを特徴とする熱交換器。
- 上記冷却流体が流れる向きは上記被冷却流体が流れる向きに対して向流であることを特徴とする請求項1記載の熱交換器。
- 上記コイル管は上記環状流路内に挿抜可能に配されることを特徴とする請求項1又は請求項2に記載の熱交換器。
- 上記環状流路において、上記コイル管より外側の外側環状流路の横断面積と、該コイル管よりも内側の内側環状流路の横断面積とが同一となるように上記コイル管のコイル平均径を設定することを特徴とする請求項1乃至請求項3の何れかに記載の熱交換器。
- 上記コイル管のコイル平均径は当該コイル管の外径の4倍以上であることを特徴とする請求項1乃至請求項4の何れかに記載の熱交換器。
- 上記コイル管に軸方向に沿って当該コイル管の全体形状及びコイルピッチを保つ保形材を設けることを特徴とする請求項1乃至請求項5の何れかに記載の熱交換器。
- 上記内装管の内部又は/及び上記外装管の外部に断熱材を配することを特徴とする請求項1乃至請求項6の何れかに記載の熱交換器。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP17899181.6A EP3415853A4 (en) | 2017-02-28 | 2017-02-28 | HEAT EXCHANGER |
PCT/JP2017/007912 WO2018158843A1 (ja) | 2017-02-28 | 2017-02-28 | 熱交換器 |
KR1020187027192A KR102294972B1 (ko) | 2017-02-28 | 2017-02-28 | 열교환기 |
JP2018548013A JP6483936B2 (ja) | 2017-02-28 | 2017-02-28 | 熱交換器 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2017/007912 WO2018158843A1 (ja) | 2017-02-28 | 2017-02-28 | 熱交換器 |
Publications (1)
Publication Number | Publication Date |
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WO2018158843A1 true WO2018158843A1 (ja) | 2018-09-07 |
Family
ID=63370393
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2017/007912 WO2018158843A1 (ja) | 2017-02-28 | 2017-02-28 | 熱交換器 |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3415853A4 (ja) |
JP (1) | JP6483936B2 (ja) |
KR (1) | KR102294972B1 (ja) |
WO (1) | WO2018158843A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110579016A (zh) * | 2019-07-31 | 2019-12-17 | 山东碳垣纳米科技有限公司 | 气体加热装置以及气体加热方法 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2023535142A (ja) * | 2020-07-13 | 2023-08-16 | アイヴィーズ インコーポレイテッド | 水素燃料供給システムおよび方法 |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51117842U (ja) * | 1973-12-13 | 1976-09-24 | ||
JPS51159959U (ja) * | 1975-06-13 | 1976-12-20 | ||
JPS54127247U (ja) * | 1978-02-25 | 1979-09-05 | ||
JPS62202995A (ja) * | 1986-03-03 | 1987-09-07 | Mitsubishi Heavy Ind Ltd | 竪型熱交換器 |
JPS63217192A (ja) * | 1987-03-05 | 1988-09-09 | Nippon Denso Co Ltd | 熱交換器の組付構造 |
JPH01170875U (ja) | 1988-05-11 | 1989-12-04 | ||
JPH0684270U (ja) | 1993-05-17 | 1994-12-02 | タバイエスペック株式会社 | 多段冷凍システム用コンデンサ |
JP2002147976A (ja) * | 2000-11-13 | 2002-05-22 | M Technique Co Ltd | 熱交換器 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA1291113C (en) * | 1985-03-22 | 1991-10-22 | Keith Stuart Mclaren | Heat exchanger |
JPH01170875A (ja) | 1987-12-25 | 1989-07-05 | Pfu Ltd | 電圧保証試験装置 |
JPH04260788A (ja) * | 1991-02-15 | 1992-09-16 | Miura Kenkyusho:Kk | 二重筒内コイル型熱交換器 |
JPH0684270A (ja) | 1992-09-04 | 1994-03-25 | Alps Electric Co Ltd | 磁気ディスク装置 |
US20030121648A1 (en) * | 2001-12-28 | 2003-07-03 | Visteon Global Technologies, Inc. | Counter-flow heat exchanger with optimal secondary cross-flow |
JP2005299940A (ja) * | 2004-04-06 | 2005-10-27 | T Rad Co Ltd | 熱交換器 |
EP2505951B1 (en) * | 2009-11-24 | 2020-12-23 | M Technique Co., Ltd. | Heat exchanger |
-
2017
- 2017-02-28 JP JP2018548013A patent/JP6483936B2/ja active Active
- 2017-02-28 EP EP17899181.6A patent/EP3415853A4/en not_active Ceased
- 2017-02-28 WO PCT/JP2017/007912 patent/WO2018158843A1/ja active Application Filing
- 2017-02-28 KR KR1020187027192A patent/KR102294972B1/ko active IP Right Grant
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51117842U (ja) * | 1973-12-13 | 1976-09-24 | ||
JPS51159959U (ja) * | 1975-06-13 | 1976-12-20 | ||
JPS54127247U (ja) * | 1978-02-25 | 1979-09-05 | ||
JPS62202995A (ja) * | 1986-03-03 | 1987-09-07 | Mitsubishi Heavy Ind Ltd | 竪型熱交換器 |
JPS63217192A (ja) * | 1987-03-05 | 1988-09-09 | Nippon Denso Co Ltd | 熱交換器の組付構造 |
JPH01170875U (ja) | 1988-05-11 | 1989-12-04 | ||
JPH0684270U (ja) | 1993-05-17 | 1994-12-02 | タバイエスペック株式会社 | 多段冷凍システム用コンデンサ |
JP2002147976A (ja) * | 2000-11-13 | 2002-05-22 | M Technique Co Ltd | 熱交換器 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3415853A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110579016A (zh) * | 2019-07-31 | 2019-12-17 | 山东碳垣纳米科技有限公司 | 气体加热装置以及气体加热方法 |
Also Published As
Publication number | Publication date |
---|---|
KR20180115760A (ko) | 2018-10-23 |
JPWO2018158843A1 (ja) | 2019-03-07 |
JP6483936B2 (ja) | 2019-03-13 |
KR102294972B1 (ko) | 2021-08-26 |
EP3415853A4 (en) | 2019-11-20 |
EP3415853A1 (en) | 2018-12-19 |
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