WO2018061531A1 - 熱交換器、ラジアントチューブ式加熱装置及び熱交換器の製造方法 - Google Patents
熱交換器、ラジアントチューブ式加熱装置及び熱交換器の製造方法 Download PDFInfo
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- WO2018061531A1 WO2018061531A1 PCT/JP2017/029965 JP2017029965W WO2018061531A1 WO 2018061531 A1 WO2018061531 A1 WO 2018061531A1 JP 2017029965 W JP2017029965 W JP 2017029965W WO 2018061531 A1 WO2018061531 A1 WO 2018061531A1
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- Prior art keywords
- heat exchanger
- heat
- conductor
- radiant tube
- peripheral surface
- Prior art date
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- 238000010438 heat treatment Methods 0.000 title claims description 27
- 238000004519 manufacturing process Methods 0.000 title claims description 22
- 238000000034 method Methods 0.000 title claims description 6
- 230000002093 peripheral effect Effects 0.000 claims abstract description 58
- 230000001737 promoting effect Effects 0.000 claims abstract description 11
- 239000004020 conductor Substances 0.000 claims description 81
- 239000007789 gas Substances 0.000 claims description 46
- 238000002485 combustion reaction Methods 0.000 claims description 16
- 239000000567 combustion gas Substances 0.000 claims description 8
- 239000000463 material Substances 0.000 claims description 6
- 238000003466 welding Methods 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 11
- 230000008646 thermal stress Effects 0.000 description 8
- 239000002737 fuel gas Substances 0.000 description 7
- 230000000052 comparative effect Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 230000035882 stress Effects 0.000 description 3
- 229910001208 Crucible steel Inorganic materials 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000000137 annealing Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000003779 heat-resistant material Substances 0.000 description 1
- 229910010272 inorganic material Inorganic materials 0.000 description 1
- 239000011147 inorganic material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/12—Radiant burners
- F23D14/126—Radiant burners cooperating with refractory wall surfaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C3/00—Combustion apparatus characterised by the shape of the combustion chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
- F23L15/00—Heating of air supplied for combustion
- F23L15/04—Arrangements of recuperators
- F23L15/045—Arrangements of recuperators using intermediate heat-transfer fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
- F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
- F23M9/003—Baffles or deflectors for air or combustion products; Flame shields in flue gas ducts
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
-
- 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
- F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
-
- 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
-
- 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
- F28F1/24—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 transversely
-
- 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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
-
- 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
-
- 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
- F28D7/1607—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
-
- 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
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
Definitions
- the present invention relates to a heat exchanger, a radiant tube heating device, and a method for manufacturing the heat exchanger.
- a radiant tube heating device in which a burner and a heat exchanger are provided in a radiant tube is known as a heating means used in a heat treatment furnace for performing heat treatment of a metal material or the like.
- the fuel gas and the combustion air are supplied to the burner to burn the fuel gas, thereby generating the combustion gas in the radiant tube, and using the generated combustion gas. Heat the radiant tube.
- a spiral heat conductor is provided on the outer peripheral surface of the heat exchanger body, and exhaust gas, which is a combustion gas after heating the radiant tube, is guided by the heat conductor while the heat exchanger body. It passes between the outer peripheral surface of the heat exchanger body and the inner peripheral surface of the radiant tube along the outer peripheral surface.
- the heat of the exhaust gas is absorbed by the outer peripheral surface of the heat exchanger body and the heat exchanger body is heated, and the heat of the exhaust gas is also absorbed by the heat conductor, and also by heat conduction from the heat conductor.
- the body is heated.
- the heat exchanger main body heated in this way the combustion air flowing through the hollow interior of the heat exchanger main body before being supplied to the burner is preheated, and this preheated combustion air is supplied to the burner.
- the combustion efficiency of fuel gas in the burner is increased.
- the present invention has been made in view of the above problems, and its purpose is to reduce the temperature difference between the heat exchanger main body and the heat conductor, and to suppress the heat conductor from being damaged. It is providing the manufacturing method of a heat exchanger, a radiant tube type heating apparatus, and a heat exchanger.
- a heat exchanger includes a hollow heat exchanger body enclosed in a radiant tube, and heat provided on the outer peripheral surface of the heat exchanger body.
- a heat exchanger for exchanging heat between a first gas flowing between the radiant tube and the heat exchanger body and a second gas flowing through a hollow interior of the heat exchanger body.
- a turbulent flow generation promoting means for accelerating the generation of turbulent flow with respect to the first gas flowing between the radiant tube and the heat exchanger main body, and welding the outer peripheral surface of the heat exchanger main body. It is characterized by being provided without.
- the heat conductor is annular, and a plurality of heat conductors are arranged at predetermined intervals in the axial direction of the heat exchanger, and the heat conductor is It is also used as a turbulent flow generation promoting means.
- the heat exchanger according to the present invention is characterized in that, in the above-mentioned invention, the heat conductor is composed of a plurality of divided members divided in the circumferential direction.
- the cross section of the heat conductor parallel to the axial direction of the heat exchanger main body is a columnar shape, a flat plate shape, or a semicircular shape. It is.
- the heat exchanger according to the present invention is characterized in that, in the above-described invention, the heat exchanger has a connecting means for connecting the circumferential ends of the plurality of divided members.
- the height from the outer peripheral surface of the heat conductor is smaller than the distance between the heat conductors adjacent in the axial direction of the heat exchanger main body. It is a feature.
- the distance between the heat conductors adjacent in the axial direction of the heat exchanger main body is P [mm]
- the height of the heat conductor from the outer peripheral surface is as described above.
- Is H [mm] the total heat transfer area of the heat exchanger main body and each heat conductor is A [mm 2 ]
- the heat transfer area of the heat conductor is Af [mm 2 ]
- 0. 10 ⁇ (H / P) 0.8 ⁇ ⁇ (A ⁇ Af) / A ⁇ ⁇ 0.20 is satisfied.
- the heat exchanger according to the present invention is characterized in that, in the above-mentioned invention, the heat conductor repeats unevenness at a constant height in the axial direction of the heat exchanger body.
- the heat conductor is an annular member having one end opened, and a plurality of heat conductors are arranged at predetermined intervals in the axial direction of the heat exchanger body.
- the heat conductor is also used as the turbulent flow generation promoting means.
- the heat exchanger according to the present invention is the heat conductor according to the above-described invention, which is configured by a plurality of divided members that are annular and divided in the circumferential direction, or an annular member that is open at one end. It is characterized by having additionally installed.
- the heat exchanger according to the present invention is characterized in that, in the above-described invention, the heat conductor is made of a material having higher heat resistance than the heat exchanger body.
- the radiant tube heating device performs heat exchange between the combustion gas inserted in the radiant tube and flowing in the radiant tube and the combustion air used to heat the radiant tube.
- the heat exchanger according to the invention described above is used as the heat exchange means.
- the heat exchanger manufacturing method includes a heat conductor that promotes heat exchange in a heat exchanger manufacturing method that performs heat exchange with combustion air using exhaust gas from a burner attached to a radiant tube.
- a heat conductor that promotes heat exchange in a heat exchanger manufacturing method that performs heat exchange with combustion air using exhaust gas from a burner attached to a radiant tube.
- the method for manufacturing a heat exchanger according to the present invention is characterized in that, in the above-described invention, the heat conductor repeats unevenness at a constant height in the axial direction of the heat exchanger body.
- the heat exchanger manufacturing method includes a heat conductor that promotes heat exchange in a heat exchanger manufacturing method that performs heat exchange with combustion air using exhaust gas from a burner attached to a radiant tube.
- a heat conductor that promotes heat exchange in a heat exchanger manufacturing method that performs heat exchange with combustion air using exhaust gas from a burner attached to a radiant tube.
- the heat conductor formed by a plurality of divided members that are annular and divided in the circumferential direction, or an annular member that is open at one end, is provided. It is characterized by this.
- the method for manufacturing a heat exchanger according to the present invention is characterized in that, in the above-described invention, the heat conductor repeats unevenness at a constant height in the axial direction of the heat exchanger body.
- the radiant tube heating device In the heat exchanger, the radiant tube heating device, and the heat exchanger manufacturing method according to the present invention, it is possible to reduce the temperature difference between the heat exchanger main body and the heat conductor, thereby suppressing the breakage of the heat conductor. There is an effect that can be done.
- Drawing 1 is a mimetic diagram showing the composition of the radiant tube type heating device concerning an embodiment.
- FIG. 2 is an enlarged view of the vicinity of the heat exchanger in the radiant tube heating device.
- FIG. 3 is a view showing a heat exchanger body in which no heat conductor is installed in the heat exchanger.
- FIG. 4 is a schematic diagram showing a configuration of a heat exchanger according to a conventional example.
- Drawing 5 is a mimetic diagram showing an example of a fin provided in a heat exchanger concerning an embodiment.
- FIG. 6 is a diagram illustrating a state in which both end portions in the circumferential direction of the upper fin and the lower fin are coupled.
- Drawing 7 is a mimetic diagram showing an example of a heat conductor provided in a heat exchanger concerning an embodiment.
- Drawing 8 is an explanatory view about the pitch and height of a fin in a heat exchanger concerning an embodiment.
- FIG. 9 is a graph showing the relationship between fin dimensional parameters, heat exchange efficiency, and exhaust gas pressure loss margin rate.
- FIG. 10 is a view showing a heat exchanger in which a heat conductor is provided on the outer peripheral surface of the heat exchanger main body so as to be uneven at a certain height in the axial direction of the heat exchanger main body.
- Drawing 1 is a mimetic diagram showing the composition of radiant tube type heating device 1 concerning an embodiment.
- FIG. 2 is an enlarged view of the vicinity of the heat exchanger 13 in the radiant tube heating device 1.
- the radiant tube type heating device 1 includes a cylindrical radiant tube 11, heats the radiant tube 11 from the inside, and heats a steel plate or a steel material by radiant heat from the outer peripheral surface of the radiant tube 11.
- a burner 12 is inserted into one end of the radiant tube 11.
- the burner 12 generates combustion gas by burning fuel gas using combustion air, and heats the radiant tube 11 from the inside using combustion gas flowing through the radiant tube 11.
- a heat exchanger 13 is inserted into the other end of the radiant tube 11. The heat exchanger 13 exchanges heat between the combustion gas (hereinafter also referred to as exhaust gas) that heated the radiant tube 11 and the combustion air supplied from the outside, and supplies the heated combustion air to the burner 12 side. To do.
- a plurality of fins 14 that are annular heat conductors that enclose the heat exchanger main body 13a are arranged side by side with a predetermined interval in the axial direction of the heat exchanger main body. ing.
- the fins 14 are provided on the heat exchanger body 13a so that the radial direction of the fins 14 is orthogonal to the axial direction of the heat exchanger body.
- the radial direction of the fins 14 is heat exchange. You may incline and provide the fin 14 with respect to the heat exchanger main body 13a so that it may cross diagonally with an axial direction of the main body.
- the fins 14 are installed without welding on the outer peripheral surface of the heat exchanger main body 13a where the heat conductor as shown in FIG. 3 is not installed. Thereby, the damage based on the temperature difference between the heat exchanger main body 13a and the fins 14 can be suppressed, and the heat transfer function of the fins 14 can be maintained for a long time.
- the heat of the exhaust gas is absorbed by the outer peripheral surface of the heat exchanger main body 13a and the heat exchanger main body 13a is heated. .
- the fins 14 absorb the heat of the exhaust gas, transfer the absorbed heat to the heat exchanger 13 by heat conduction, and heat the heat exchanger 13. Thereby, compared with the case where the fin 14 is not provided on the outer peripheral surface of the heat exchanger 13, heat transfer from the exhaust gas to the heat exchanger 13 can be promoted, and the amount of heat transfer to the heat exchanger 13 can be increased. it can.
- the heat exchanger body 13a heated in this manner preheats the combustion air flowing through the hollow interior of the heat exchanger body 13a before being supplied to the burner 12, and this preheated combustion air is supplied to the burner 12.
- the combustion efficiency of the fuel gas in the burner 12 is increased.
- the fuel gas usage ratio in the burner 12 can be reduced.
- the fins 14 function as heat transfer promoting bodies that promote heat transfer from the exhaust gas to the heat exchanger body 13a.
- the exhaust gas that passes between the outer peripheral surface of the heat exchanger main body 13a and the inner peripheral surface of the radiant tube 11 and is absorbed by the heat exchanger main body 13a and the fins 14 is discharged from the exhaust port 6 provided in the radiant tube 11. Is done.
- the fin 14 promotes the generation of turbulent flow with respect to the exhaust gas flowing between the inner peripheral surface of the radiant tube 11 and the outer peripheral surface of the heat exchanger main body 13a. It also functions as a turbulent flow generation promoting body.
- FIG. 4 is a schematic diagram showing a configuration of a heat exchanger 113 according to a conventional example.
- spiral fins 114 are provided on the outer peripheral surface of the heat exchanger main body 113a over the axial direction of the heat exchanger main body 113a.
- the exhaust gas passes between the outer peripheral surface of the heat exchanger main body 113a and the inner peripheral surface of the radiant tube 11 along the outer peripheral surface of the heat exchanger main body 113a.
- the turbulent flow is generated by the spiral fins 114 with respect to the exhaust gas flowing between the outer peripheral surface of the heat exchanger main body 113a and the inner peripheral surface of the radiant tube 11, it is near the outer peripheral surface of the heat exchanger main body 113a.
- the effect of generating turbulence is small, and the exhaust gas having a low temperature absorbed by the heat exchanger body 113a flowing in the vicinity of the outer peripheral surface of the heat exchanger body 113a and the exhaust gas having a high temperature flowing in the vicinity of the inner peripheral surface of the radiant tube 11 Replacement is not done actively.
- the turbulent flow is actively generated by the fins 14 with respect to the exhaust gas, so that the inner peripheral surface of the radiant tube 11 and the heat exchanger main body.
- a low temperature exhaust gas absorbed by the heat exchanger body 13a flowing near the outer peripheral surface of the heat exchanger body 13a and a high temperature exhaust gas flowing near the inner peripheral surface of the radiant tube 11 Is being actively exchanged.
- the effect of generating the turbulent flow in the vicinity of the outer peripheral surface of the heat exchanger main body 113a is small with respect to the exhaust gas by the fins 14.
- the amount of heat transferred from the exhaust gas to the heat exchanger 13 can be increased. Therefore, the temperature difference between the heat exchanger main body 13a and the fins 14 can be reduced correspondingly, and damage to the fins 14 due to the difference in thermal expansion between the heat exchanger main body 13a and the fins 14 can be suppressed. Moreover, since the damage of the fins 14 can be suppressed in this way, the life of the fins 14 can be extended, and deterioration of the heat transfer efficiency improvement effect from the exhaust gas to the heat exchanger body 13a due to the damage of the fins 14 can be suppressed. .
- FIG. 5 is a schematic diagram illustrating an example of the fins 14 provided in the heat exchanger 13 according to the embodiment.
- the fin 14 shown in FIG. 5 includes an upper fin 14a and a lower fin 14b which are two divided members divided in half in the circumferential direction.
- the fin 14 may be divided into three or more in the circumferential direction.
- operativity which attaches or removes the fin 14 with respect to the heat exchanger main body 13a can be improved.
- the fins 14 are divided into a plurality in the circumferential direction, generation of thermal stress due to thermal expansion can be suppressed, and the life of the fins 14 can be extended.
- FIG. 6 is a diagram showing a state in which both circumferential ends of the upper fin 14a and the lower fin 14b are connected. As shown in FIG. 6, both ends in the circumferential direction of the upper fin 14a and the lower fin 14b are fastened and connected by bolts 20A and 20B and nuts 21A and 21B, respectively.
- the fins 14 and the heat exchanger main body 13a are controlled by the tightening amounts of the bolts 20A and 20B so that the stress generated by the heat exchanger 13 and the fins 14 being pressed against each other due to thermal expansion is not excessively increased. It is possible to adjust in advance the stress generated by the contact with. Therefore, when the heat exchanger 13 and the fin 14 are thermally expanded, it is possible to suppress the stress generated by the mutual pressing from being excessively increased and the fin 14 from being damaged.
- the connecting means for connecting the circumferential end portions of the upper fin 14a and the lower fin 14b is not limited to those using fastening members such as bolts 20A and 20B and nuts 21A and 21B.
- a clamping member such as a clip
- the circumferential ends of the upper fin 14a and the lower fin 14b may be fixed and connected.
- the fins 14 having a columnar cross section parallel to the axial direction of the heat exchanger main body are used, but the shape of the cross section is the columnar shape.
- a fin 14 having a flat plate shape or a semicircular shape having a smaller thickness may be used.
- FIG. 7 is a schematic diagram illustrating an example of a heat conductor provided in the heat exchanger 13 according to the embodiment.
- a fin 14 ⁇ / b> A configured by an annular member (C-shaped member) having an open end 14 ⁇ / b> A ⁇ b> 1 as shown in FIG. 7 may be used.
- the fin 14A since the one end portion 14A1 is opened, the workability of attaching and detaching the fin 14A to and from the heat exchanger body 13a in which the heat conductor as shown in FIG. 3 is not installed is improved. be able to.
- the one end portion 14A1 of the fin 14A is open, generation of thermal stress due to thermal expansion can be suppressed, and the life of the fin 14A can be extended.
- the material used for the fins 14 and 14A it is desirable to use a material having higher heat resistance than the material used for the heat exchanger body 13a.
- heat-resistant cast steel is used for the heat exchanger body 13a, but a heat-resistant material having a higher Ni ratio and higher heat resistance than the heat-resistant cast steel used for the heat exchanger body 13a is used for the fins 14 and 14A.
- FIG. 8 is an explanatory diagram of the pitch and height of the fins 14 in the heat exchanger 13 according to the embodiment.
- FIG. 9 is a graph showing the relationship between the dimensional parameters of the fins 14, the heat exchange efficiency, and the exhaust gas pressure loss margin rate.
- Table 1 shows the relationship between the dimensional parameters of the fins 14, the heat exchange efficiency, and the exhaust gas pressure loss margin rate.
- P is a fin pitch that is a distance between adjacent fins 14 in the axial direction of the heat exchanger body, and from the outer peripheral surface of the heat exchanger body 13 a.
- the fin height is H
- the total heat transfer area that is the total surface area that can be in contact with the exhaust gas of the heat exchanger main body 13a and each fin 14 is A
- the fin is the total surface area that can be in contact with the exhaust gas of each fin 14
- the dimensional parameter (H / P) of the fin 14 (H / P) 0.8 ⁇ ⁇ (A ⁇ Af) / A ⁇ satisfies the following mathematical formula (1).
- the exhaust gas pressure loss margin ratio decreases as the fin height H increases, regardless of the length of the fin pitch P. If the exhaust gas pressure loss margin ratio becomes too small, in other words, if the exhaust gas pressure loss becomes too large, the exhaust gas hardly flows between the heat exchanger body 13a provided with the fins 14 on the outer peripheral surface and the radiant tube 11. Therefore, the exhaust gas pressure loss margin rate is preferably set to 100 [%] or more. At this time, the fin height H and the fin pitch P are preferably such that the heat exchange efficiency is 1.0% or more.
- the thermal expansion difference between the fins 14 and the heat exchanger body 13a is reduced while ensuring sufficient heat exchange efficiency and exhaust gas pressure loss margin rate. Thus, breakage of the fins 14 can be suppressed.
- Table 2 shows heat exchangers in Examples 1 to 3 in which the dimension parameter of the fin 14 satisfies the relationship of the above formula (1) and the comparative example in which the dimension parameter of the fin 14 does not satisfy the relationship of the above formula (1).
- the relationship between the surface temperature of the main body 13a and the fin 14 and the generated thermal stress ratio is shown.
- Example 1 is the condition of “No. 2” in Table 1
- Example 2 is the condition of “No. 5” in Table 1
- Example 3 is the condition of “No. 3” in Table 1.
- the comparative example applies the condition of “No. 1” in Table 1.
- the “generated thermal stress ratio” relates to the thermal stress generated between the heat exchanger body 13a and the fins 14, and in Examples 1 to 3 and the comparative example, the fins 14 and the heat exchanger body.
- the difference of the surface temperature with 13a was calculated
- the difference in surface temperature between the fin 14 and the heat exchanger body 13a is smaller than in the comparative example, and the generated thermal stress ratio is smaller than in the comparative example. Therefore, it turns out that the thermal stress which generate
- the surface temperatures of the heat exchanger main body 13a and the fins 14 are higher in the order of the first embodiment, the second embodiment, and the third embodiment. This is because the heat transfer efficiency from the exhaust gas to the heat exchanger main body 13a and the fins 14 is increased in the order of Example 2 and Example 3.
- the fins 14L of the fins 14H of fin height H 1 from the outer peripheral surface of the heat exchanger body 13a is 10 [mm]
- the fin height H 2 of the outer peripheral surface of the heat exchanger body 13a is 5 [mm]
- the fins 14H and 14L for example, a heat conductor formed of a plurality of divided members that are annular and divided in the circumferential direction or an annular member that is open at one end can be used. Thereby, the turbulent flow promotion effect by the fins 14H and 14L becomes large, and the heat transfer efficiency from the exhaust gas to the heat exchanger main body 13a and the fins 14H and 14L can be further increased.
- a plurality of divided members for example, fins 14 that are annular and divided in the circumferential direction with respect to the heat exchanger 13 in which the fins 14 are installed on the outer peripheral surface of the heat exchanger main body 13a as shown in FIG.
- the heat exchanger 13 has a plurality of divisions which are annular and divided in the circumferential direction on the outer peripheral surface of the heat exchanger main body 13a in which no heat conductor is installed as shown in FIG. It can manufacture by providing heat conductors, such as fins 14 and 14A comprised by the member or the annular member by which the one end part was open
- the heat exchanger 13 has a plurality of divided members or one end portion which is annular and divided in the circumferential direction with respect to the heat exchanger main body 13a where the heat conductor is already installed. It can manufacture by providing heat conductors, such as fins 14 and 14A comprised by the open annular member. Thereby, additional installation of a heat conductor becomes easy with respect to the heat exchanger main body 13a, and it becomes possible to change to the heat exchanger 13 with higher heat transfer efficiency.
- the heat exchanger 13 is attached to the outer peripheral surface of the heat exchanger main body 13a where the heat conductor is not installed or the outer peripheral surface of the heat exchanger main body 13a where the heat conductor is already installed.
- the heat conductor may be provided with unevenness at a certain height in the axial direction of the heat exchanger body.
- the effect of promoting turbulence is further increased, the heat transfer efficiency is increased, and the heat exchange efficiency of the heat exchanger 13 can be increased. .
- the turbulent flow generation promoting body that promotes the generation of turbulent flow with respect to the exhaust gas flowing between the inner peripheral surface of the radiant tube 11 and the outer peripheral surface of the heat exchanger main body 13a is separate from the fins 14 and You may provide in an outer peripheral surface.
- the present invention can be applied.
- the heat exchanger which can make the temperature difference of a heat exchanger main body and a heat conductor small, and can suppress the failure
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Abstract
Description
11 ラジアントチューブ
12 バーナ
13 熱交換器
13a 熱交換器本体
14 フィン
14a 上部フィン
14b 下部フィン
14A フィン
14A1 一端部
14H フィン
14L フィン
20A ボルト
20B ボルト
21A ナット
21B ナット
113 熱交換器
113a 熱交換器本体
114 螺旋状フィン
Claims (16)
- ラジアントチューブに内包される中空状の熱交換器本体と、
前記熱交換器本体の外周面に設けられた熱伝導体とを備えており、
前記ラジアントチューブと前記熱交換器本体との間を流れる第一気体と、前記熱交換器本体の中空内部を流れる第二気体との間で熱交換を行う熱交換器において、
前記ラジアントチューブと前記熱交換器本体との間を流れる前記第一気体に対して、乱流の発生を促進させる乱流発生促進手段を、前記熱交換器本体の外周面に溶接をしないで設けたことを特徴とする熱交換器。 - 請求項1に記載の熱交換器において、
前記熱伝導体は環状であって、熱交換器本体軸線方向に所定間隔をあけて複数配置されており、
前記熱伝導体を前記乱流発生促進手段として兼用することを特徴とする熱交換器。 - 請求項2に記載の熱交換器において、
前記熱伝導体は周方向で分割された複数の分割部材で構成されていることを特徴とする熱交換器。 - 請求項3に記載の熱交換器において、
前記熱伝導体の熱交換器本体軸線方向と平行な断面が、柱形状、平板形状または半円形状であることを特徴とする熱交換器。 - 請求項3または4に記載の熱交換器において、
前記複数の分割部材の周方向端部を連結する連結手段を有することを特徴とする熱交換器。 - 請求項2乃至5のいずれか一つに記載の熱交換器において、
熱交換器本体軸線方向で隣り合う熱伝導体間の距離よりも、前記熱伝導体の前記外周面からの高さが小さいことを特徴とする熱交換器。 - 請求項2乃至6のいずれか一つに記載の熱交換器において、
熱交換器本体軸線方向で隣り合う熱伝導体間の距離をP[mm]とし、前記熱伝導体の前記外周面からの高さをH[mm]とし、前記熱交換器本体及び各熱伝導体の全伝熱面積をA[mm2]とし、前記熱伝導体の伝熱面積をAf[mm2]としたとき、0.10≦(H/P)0.8・{(A-Af)/A}≦0.20の関係を満たすことを特徴とする熱交換器。 - 請求項2乃至5のいずれか一つに記載の熱交換器において、
熱交換器本体軸線方向に前記熱伝導体が一定の高さで凹凸を繰り返していることを特徴とする熱交換器。 - 請求項1に記載の熱交換器において、
前記熱伝導体は一端部が開放された環状部材であって、熱交換器本体軸線方向に所定間隔をあけて複数配置されており、
前記熱伝導体を前記乱流発生促進手段として兼用することを特徴とする熱交換器。 - 請求項2に記載の熱交換器において、
環状であって周方向で分割された複数の分割部材、または、一端部が開放された環状部材、によって構成された前記熱伝導体を追加で設置したことを特徴とする熱交換器。 - 請求項1乃至10のいずれか一つに記載の熱交換器において、
前記熱交換器本体よりも耐熱性の高い材料で前記熱伝導体を構成したことを特徴とする熱交換器。 - ラジアントチューブ内に挿入された、該ラジアントチューブ内を流れる燃焼ガスと該ラジアントチューブを加熱するために用いられる燃焼空気との間で熱交換を行う熱交換手段を備えるラジアントチューブ式加熱装置において、
前記熱交換手段として、請求項1乃至11のいずれか一つに記載の熱交換器を用いたことを特徴とするラジアントチューブ式加熱装置。 - ラジアントチューブに取り付けられたバーナの排ガスを利用して燃焼空気と熱交換を行う熱交換器の製造方法において、
熱交換を促進する熱伝導体が設置されていない中空状の熱交換器本体の外周面に、環状であって周方向で分割された複数の分割部材、または、一端部が開放された環状部材、によって構成された前記熱伝導体を設けたことを特徴とする熱交換器の製造方法。 - 請求項13に記載の熱交換器の製造方法において、
熱交換器本体軸線方向に前記熱伝導体が一定の高さで凹凸を繰り返していることを特徴とする熱交換器の製造方法。 - ラジアントチューブに取り付けられたバーナの排ガスを利用して燃焼空気と熱交換を行う熱交換器の製造方法において、
熱交換を促進する熱伝導体が設置された熱交換器本体に、環状であって周方向で分割された複数の分割部材、または、一端部が開放された環状部材、によって構成された前記熱伝導体を追加して設けたことを特徴とする熱交換器の製造方法。 - 請求項15に記載の熱交換器の製造方法において、
熱交換器本体軸線方向に前記熱伝導体が一定の高さで凹凸を繰り返していることを特徴とする熱交換器の製造方法。
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US16/337,109 US11209225B2 (en) | 2016-09-29 | 2017-08-22 | Heat exchanger, radiant tube type heating device, and method of manufacturing heat exchanger |
MX2019003589A MX2019003589A (es) | 2016-09-29 | 2017-08-22 | Intercambiador de calor, dispositivo de calentamiento de tipo tubo radiante, y metodo de fabricacion de intercambiador de calor. |
CN201780058847.7A CN109790980B (zh) | 2016-09-29 | 2017-08-22 | 热交换器、辐射管式加热装置以及热交换器的制造方法 |
KR1020197008397A KR102229433B1 (ko) | 2016-09-29 | 2017-08-22 | 열교환기, 라디언트 튜브식 가열 장치 및 열교환기의 제조 방법 |
JP2017557030A JP6477920B2 (ja) | 2016-09-29 | 2017-08-22 | 熱交換器、ラジアントチューブ式加熱装置及び熱交換器の製造方法 |
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KR20190040312A (ko) | 2019-04-17 |
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US20190219346A1 (en) | 2019-07-18 |
US11209225B2 (en) | 2021-12-28 |
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