WO2013150818A1 - 伝熱管とそれを用いた熱交換器 - Google Patents
伝熱管とそれを用いた熱交換器 Download PDFInfo
- Publication number
- WO2013150818A1 WO2013150818A1 PCT/JP2013/053192 JP2013053192W WO2013150818A1 WO 2013150818 A1 WO2013150818 A1 WO 2013150818A1 JP 2013053192 W JP2013053192 W JP 2013053192W WO 2013150818 A1 WO2013150818 A1 WO 2013150818A1
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- WIPO (PCT)
- Prior art keywords
- tube
- heat transfer
- support member
- pipe
- diameter
- 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
- F28D7/10—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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- 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
- F28D1/06—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 the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
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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
- F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
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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
- F28D7/026—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 and formed by bent members, e.g. plates, the coils having a cylindrical configuration
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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
- 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
- F28F1/122—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 being formed of wires
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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
- 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
- F28F1/405—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 and being formed of wires
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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
- 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
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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
- 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
- F28F9/02—Header boxes; End plates
- F28F9/0229—Double end plates; Single end plates with hollow spaces
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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
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/04—Fastening; Joining by brazing
Definitions
- the present invention relates to a heat transfer tube and a heat exchanger such as a multi-tube type using the heat transfer tube.
- a double-tube type that exchanges heat between the fluid that passes through the inner tube and the fluid that flows between the inner tube and the outer tube through the inner tube.
- a heat exchanger There is a heat exchanger.
- This heat exchanger is applied to a heat pump type water heater or a heater using a refrigerant, a high-temperature and high-pressure refrigerant circulates in the inner pipe, and heats water flowing between the inner pipe and the outer pipe to supply hot water.
- Patent Document 1 a plurality of double pipes inserted through the inner pipe are juxtaposed in parallel in the outer pipe, and at the end thereof, the inner header pipe is joined to communicate the outer pipe, The inner pipe that penetrates the inner header pipe is joined and communicated with the outer header pipe, making it possible to use a small-diameter pipe by greatly reducing the pressure loss of the fluid.
- the configuration is easy to incorporate.
- the above conventional double pipe heat exchanger uses pipes with small diameters of the inner pipe and the outer pipe in order to realize compactness, but the fluid is surely provided in the gap portion between the outer pipe and the inner pipe. It is necessary to be configured so that heat can be transferred to the pipe, and manufacturing at the joint portion between the outer pipe, the inner pipe, and the header pipe requires accuracy.
- joining of such tube bodies is performed by brazing, but the solder may overflow and flow due to heating at the time of joining, and the wax flowing out to the outside is visible, but a double tube structure Therefore, when it flows into the pipe, visual inspection is impossible, and if it enters the gap between the inner pipe and the outer pipe, the flow path is disturbed, that is, the cross-sectional area of the flow path is not constant.
- the double pipe heat exchanger of Patent Document 1 has a space in which the center of the inner pipe forms a straight line and the resistance of the heat medium flow is small, but the amount of the heat medium that flows without touching the inner pipe is large. There was a problem that heat exchange could not be performed efficiently.
- the present invention has been made in view of the above circumstances, and its purpose is to obtain a heat transfer tube in which the outer tube and the inner tube are accurately assembled in a compact heat exchanger and the heat transfer efficiency is not lowered.
- An object of the present invention is to provide a heat transfer tube capable of increasing the heat exchange efficiency between the inner tube and the heat medium flowing therethrough, and a heat exchanger using the heat transfer tube.
- the heat transfer tube 11 includes an outer tube 13, An inner tube 15 inserted into the outer tube 13; A gap support member that is disposed in a gap W between the inner peripheral surface of the outer tube 13 and the outer peripheral surface of the inner tube 15 and is made of a wire that spirally contacts the inner peripheral surface and the outer peripheral surface over substantially the entire length of the outer tube 13. 17 and A support member 19 made of a wire that spirally contacts the inner peripheral surface of the inner tube 15 over the entire length of the inner tube 15; It is characterized by comprising.
- the inner tube 15 serving as the primary flow path has a structure in which the support member 19 is supported from the inside, and the inner tube 15 and the outer tube 13 are supported by the gap support member 17,
- This gap support member 17 is positioned so that the secondary flow path, which is a pipe-shaped gap having an annular cross section, becomes an equivalent gap in the circumferential direction, so that the outer pipe 13 and the inner pipe 15 can be connected to each other during assembly. Arrangement accuracy is improved and the assembly process can be simplified. In addition, the arrangement positions of the outer pipe 13 and the inner pipe 15 are not biased, the flow passage cross-sectional area is determined, and the heat transfer efficiency is not lowered.
- the heat transfer tube 11 according to claim 2 is the heat transfer tube 11 according to claim 1,
- the gap support member 17 is made of a coil material, and has a wire diameter d1 substantially equal to the gap W.
- the outer tube 13 and the inner tube 15 can be easily assembled while keeping the gap constant by a gap support member 17 made of a coil material, and a flow path is secured with a constant gap. Is possible.
- the gap support member 17 is also interposed for heat transfer, and the heat transfer area is set large.
- the heat transfer tube 11 according to claim 3 is the heat transfer tube 11 according to claim 1,
- the gap support member 45 is made of a coil material in which small-diameter portions 43 and large-diameter portions 41 are alternately formed.
- the wire diameter d1 is smaller than the gap W, and the coil inner diameter D1 in the small-diameter portion 43 is the inner tube 15.
- the outer diameter D5 of the outer tube 13 is set to be the outer diameter D4 of the outer tube 13, and the inner tube 15 is supported in the outer tube 13.
- the small diameter portion 43 of the gap support member 45 supports the inner tube 15, and the large diameter portion 41 supports the inner peripheral surface of the outer tube 13. Since the wire diameter d1 of the gap support member 45 and the gap 47 are interposed in the gap portion W with the inner peripheral surface of the thirteen, the flow path area can be sufficiently secured.
- the heat transfer tube 11 includes an outer tube 13, An inner tube 15 inserted into the outer tube 13;
- a gap support is provided in the gap 31 between the outer peripheral surface 32 of the outer tube and the outer peripheral surface 30 of the inner tube, and is formed of a wire material that contacts the outer peripheral surface 32 of the outer tube and the outer peripheral surface 30 of the outer tube in a spiral shape over the entire length of the outer tube 13 Member 17;
- a support member 19 made of a wire that spirally contacts the inner peripheral surface 38 of the inner tube over the entire length of the inner tube 15;
- a heat transfer member 20 provided at the center of the support member 19 over the entire length of the support member 19 and having at least a part of the outer periphery in contact with the support member 19; It is characterized by comprising.
- the heat medium flowing in the inner tube 15 flows while contacting the heat transfer member 20 provided inside the inner tube 15 and contacting the support member 19, thereby
- resistance is added to the flow, and the flow becomes a meandering flow.
- the heat medium comes into contact with the heat transfer member 20, the support member 19, and the inner pipe inner peripheral surface 38 by coming into contact with the heat transfer member 20, and the heat transfer member 20, the support member 19, and the inner pipe. Heat is transferred to 15 and heat exchange is performed.
- the amount of heat exchanged is transferred to the outer peripheral surface 30 of the inner tube by heat conduction, and is exchanged with a heat medium of another system flowing through the gap 31 between the outer tube 13 and the inner tube 15. That is, the amount of heat exchanged with the heat transfer member 20 newly contributes to the improvement of the heat exchange efficiency.
- the heat transfer tube 11 according to claim 5 of the present invention is the heat transfer tube 11 according to claim 4,
- the heat transfer member 20 is
- the support member 19 is a strip 141 long in the longitudinal direction and twisted in a spiral shape.
- the strip 141 is provided in a spiral shape in contact with the support member 19, and the heat medium flowing in the inner tube 15 advances through the inner tube 15 while rotating spirally.
- the contact area and contact time when a heat medium contacts the heat-transfer member 20 can be increased.
- the heat transfer tube 11 according to claim 6 of the present invention is the heat transfer tube 11 according to claim 4,
- the heat transfer member 20 is
- the support member 19 is an outer peripheral bulging round bar 153 having an oval part 155 that is deformed by crushing a circular outer periphery at predetermined intervals in the longitudinal direction.
- the round bar material is crushed so as to be sandwiched from the direction orthogonal to the axis, so that the crushed portion bulges outward in the radial direction and becomes an oval part 155.
- the bulging tip side of the oval part 155 is brought into contact with the support member 19.
- the heat transfer tube 11 according to claim 7 of the present invention is the heat transfer tube 11 according to claim 4,
- the heat transfer member 20 is
- the support member 19 is a different-diameter round bar 161 in which a circular outer periphery is alternately formed by small-diameter portions 159 and large-diameter portions 157 at predetermined intervals in the longitudinal direction.
- the different diameter round bar 161 is inserted into the inner tube 15, so that the heat medium flowing along the different diameter round bar 161 flows while colliding with the large diameter portion 157. This collision disturbs the flow of the heat medium and reduces the heat medium that passes without contacting the inner peripheral surface 38 of the inner tube and the heat transfer member 20.
- the heat transfer tube 11 according to claim 8 of the present invention is the heat transfer tube 11 according to claim 4,
- the heat transfer member 20 is It is a solid bar 165 having a polygonal cross section.
- the position of contact with the heat medium can be made at a plurality of positions as compared with the strip 141 whose main surface only contacts the heat medium.
- the cross-sectional shape is a star or the like, the contact area can be further increased without reducing the flow path.
- a heat exchanger 49 according to claim 9 of the present invention is a heat exchanger 49 using the heat transfer tube 11 according to any one of claims 1 to 8,
- a plurality of the heat transfer tubes 11 are arranged in parallel with each other, All the inner pipe inlet ends are connected to the primary branch pipe 21 and all the inner pipe outlet ends are connected to the primary collecting pipe 27 to constitute the primary flow path, All the outer pipe inlet ends are connected to the secondary branch pipe 25 and all the outer pipe outlet ends are connected to the secondary collecting pipe 29 to form a secondary flow path.
- this heat exchanger 49 a plurality of heat transfer tubes 11 are formed in parallel to each other, arranged in close proximity on the same plane, and the outer tube 13 and the inner tube 15 are arranged. Then, the heat exchanger 49 configured on this plane can be stacked as a single unit and formed in a plurality of stages, and a heat exchanger with a small grounding area can be configured while expanding the heat transfer area. Moreover, in the heat exchanger 49 provided with the heat transfer member 20, the heat medium flowing through the inner tube 15 flows while contacting the heat transfer member 20 provided inside the inner tube 15, and conventionally, the inner peripheral surface of the inner tube. The contact area of the heat medium that has been in contact with only 38 increases.
- heat exchange with the heat transfer member 20 is performed by heat transfer.
- the amount of heat exchanged is transferred to the inner tube 15 by heat conduction, and is exchanged with a heat medium of another system flowing through the gap 31 between the outer tube 13 and the inner tube 15. That is, the amount of heat exchanged with the heat transfer member 20 newly contributes to the improvement of the heat exchange efficiency.
- a plurality of heat transfer tubes 11 including the outer tube 13 and the inner tube 15 are formed in parallel to each other, and are arranged close to each other on the same plane.
- the heat exchanger 49 configured on this plane can be stacked as a single unit in a plurality of stages, and the ground contact area can be reduced while increasing the heat transfer area.
- a heat exchanger 65 according to claim 10 is a heat exchanger using the heat transfer tube 11 according to any one of claims 1 to 8,
- a plurality of heat transfer tubes 11 are bundled, the bundle of heat transfer tubes 11 is accommodated in a cylindrical shell 67, and the inlet ends and the outlet ends of the inner tube 15 are connected to form a primary flow path.
- the inlet ends and the outlet ends of the outer tube 13 are connected to each other to form a secondary flow path, and the inside of the shell 67 is configured as a tertiary flow path.
- the bundled heat transfer tubes 11 are heat-exchanged in the cylindrical shell 67 by the outer tube 13 and the inner tube 15, and are also heat-exchanged with the heat medium flowing in the shell 67. Is possible.
- the heat exchanger 65 according to claim 11 is the heat exchanger 65 according to claim 10,
- a plurality of rectifying plates 87 having a surface perpendicular to the longitudinal direction of the heat transfer tube 11 are provided in the shell 67 to support each heat transfer tube 11 and meander the tertiary flow path. .
- the heat medium flowing in the shell 67 meanders by the rectifying plate 87, and the tertiary flow path is formed long, while the heat transfer tubes 11 in the shell 67 are substantially orthogonal to the longitudinal direction. And heat exchange is performed by increasing the heat transfer area with the outer tube 13 of each heat transfer tube 11.
- the inner tube and the outer tube are supported by the gap support member, and the gap support member has a secondary flow path that is a pipe-shaped gap having an annular cross section. Since the gaps are located in the circumferential direction, the arrangement accuracy of the outer pipe and the inner pipe during assembly is improved, and the assembly process can be simplified. In addition, by having the gap support member and the support member, the positions of the inner tube and the outer tube are not displaced, and the respective positions can be fixed without causing uneven or overflowing of the solder when brazing each other. .
- the gap support member and the support member have a structure that supports the inner tube wall and the outer tube wall, the thickness of the inner tube and the outer tube can be reduced, thereby further improving the thermal conductivity. Further, it is possible to further reduce the size of the heat exchanger. Further, the arrangement positions of the outer pipe and the inner pipe are not biased, and are located coaxially, so that the cross-sectional area of the flow path is fixed and the heat transfer efficiency is not lowered. Furthermore, since the flow path is formed in a spiral shape, the fluid in the pipe flows smoothly in the pipe axis direction, and heat is uniformly transferred to the entire pipe wall, and the gap support member and the support member become heat transfer bodies. It becomes possible to improve the heat transfer efficiency.
- the outer tube and the inner tube can be easily assembled while keeping the gap constant by being constituted by the gap support member made of a coil material, that is, When inserting and fitting each other, the gap support member serves as a guide, so that assembly can be performed with ease and accuracy, and a flow path can be secured with a certain gap.
- the small diameter portion of the gap support member supports the inner tube, and the large diameter portion supports the inner peripheral surface of the outer tube. Since the wire diameter and the gap of the gap support member are interposed in the gap portion with the inner peripheral surface, a sufficient flow path area can be ensured.
- the inner tube and the outer tube are supported by the gap support member, and the gap support member becomes a pipe-shaped gap having an annular cross section. Since the passages are positioned as equal gaps in the circumferential direction, the arrangement accuracy of the outer pipe and the inner pipe during assembly is improved, and the assembly process can be simplified. In addition, by having the gap support member and the support member, the positions of the inner tube and the outer tube are not displaced, and the respective positions can be fixed without causing uneven or overflowing of the solder when brazing each other. .
- the gap support member and the support member have a structure that supports the inner tube wall and the outer tube wall, the thickness of the inner tube and the outer tube can be reduced, thereby further improving the thermal conductivity. Further, it is possible to further reduce the size of the heat exchanger. Further, the heat transfer member supports the support member, and the support member can be brought into close contact with the inner tube. The arrangement positions of the outer tube and the inner tube are not biased, and are positioned coaxially, so that the cross-sectional area of the flow path is fixed and the heat transfer efficiency is not lowered.
- the flow path is formed in a spiral shape by the gap support member and the support member and flows in a meandering manner by the heat transfer member, the fluid in the tube in the tube axis direction sufficiently contacts and flows, and the entire tube wall
- the gap support member, the support member, and the heat transfer member become heat transfer bodies, respectively, and the heat transfer efficiency can be improved.
- the heat medium in the inner tube is spirally swirled by a spirally twisted belt plate with an inexpensive material without relatively increasing flow loss. And the heat exchange rate with the heat medium flowing through the inside can be increased.
- the bulging tip side of the oval part bulging outward in the radial direction contacts the support member, and this oval part can stir and meander the flow path of the heat medium.
- the heat exchange rate of the heat medium flowing in the inner pipe can be increased.
- the large diameter portion and the small diameter portion of the different-diameter round bar can be used to stir the heat medium flowing in the inner tube, making it easy to contact the inner tube and the heat transfer member, Increases heat exchange rate.
- the heat exchange rate between the heat medium, the heat transfer member, and the support member can be increased by increasing the surface area of the heat transfer member.
- the heat exchanger according to claim 9 of the present invention a large number of heat transfer tubes of a certain length are arranged on the same plane, and the heat transfer area of the primary heat medium and the secondary heat medium is widened with a limited installation area. And a space-saving heat exchanger with high temperature efficiency can be obtained.
- this planar heat exchanger can be stacked in multiple stages as a unit, increasing the heat exchange efficiency between the inner pipe and the heat medium flowing through it, and highly efficient with a small installation area
- the heat exchanger can be configured.
- the mutual arrangement positions of the inner pipe and the outer pipe can be accurately configured by the gap support member or the support member, and even if each is configured as a bundle, the primary flow path and the secondary flow There is no unevenness in the path, and a plurality of heat transfer tubes are bundled and arranged in a cylindrical shell, enabling reliable heat exchange with three types of heat medium in the inner tube, outer tube, and shell. Become.
- the heat medium flowing in the shell meanders by the rectifying plate provided in the shell, and the heat transfer area to the heat transfer tube can be increased.
- FIG. 2A is a schematic enlarged cross-sectional view of a heat transfer tube according to the present invention
- FIG. FIG. 4A is a plan view of a heat transfer tube array unit including heat transfer tubes according to the present invention
- FIG. 5B is a cross-sectional view taken along line BB in the plan view.
- FIG. 3 is a cross-sectional side view of the heat transfer tube array unit shown in FIG.
- FIG. 3 is a partially enlarged cross-sectional view of the cross-sectional view shown in FIG. It is sectional drawing of the heat exchanger tube of other embodiment.
- (A) is a schematic enlarged sectional view of the heat transfer tube according to the present invention
- (b) is an AA sectional view of (a).
- FIG. 7 (A) is a top view of the heat exchanger tube array unit which consists of a heat exchanger tube concerning this invention
- (b) is sectional drawing of the surface orthogonal to a primary branch pipe and including the axis line of an inner tube. It is a front view of an outer pipe and an inner pipe seen from the inner side of a secondary branch pipe. It is a principal part enlarged view of FIG.7 (b).
- (A) is a cross-sectional view of a heat transfer tube provided with a heat transfer member formed by twisting a strip 90 ° at a predetermined length
- (b) is a cross-sectional view along BB of (a)
- (c) is (a) FIG. It is a perspective view of the heat-transfer member shown in FIG.
- FIG. 12 It is the perspective view of the outer peripheral part bulging round bar which changed the direction 90 degree
- A is a cross-sectional view of the heat transfer tube provided with the outer peripheral bulge round bar of FIG. 12,
- (b) is a DD cross-sectional view of (a),
- (c) is an EE cross-sectional view of (a),
- D) is a FF sectional view of (a).
- FIG. (A) is a cross-sectional view of a heat transfer tube provided with different-diameter round bars in which large-diameter portions and small-diameter portions are alternately formed
- (b) is a GG cross-sectional view of (a)
- (c) is (a)
- FIG. (A) is a cross-sectional view of a heat transfer tube provided with a round bar with a constriction in which a large-diameter portion and a small-diameter portion are formed with gentle surfaces
- (b) is a cross-sectional view taken along II of (a)
- (c) is It is JJ sectional drawing of (a).
- (A) is a cross-sectional view of a heat transfer tube provided with a solid bar having a polygonal cross section
- (b) is a KK cross-sectional view of (a).
- FIG. 1A is a schematic enlarged cross-sectional view of a heat transfer tube according to the present invention
- FIG. 2B is a cross-sectional view taken along line AA.
- FIG. 2 is a view of a heat exchanger comprising a heat transfer tube according to the present invention.
- FIG. 3A is a plan view of the heat tube array unit
- FIG. 3B is a cross-sectional view taken along line BB in the plan view
- the heat transfer tube 11 includes an outer tube 13, an inner tube 15, a gap support member 17, and a support member 19.
- the outer tube 13 is a straight thin tube, and the inner tube 15 is inserted into the outer tube 13, and both ends are led out from both ends of the outer tube 13.
- the inner tube 15 and the outer tube 13 are coaxial.
- the heat transfer tubes 11 are composed of a plurality of tubes, are arranged in parallel so as to be in the same plane, are arranged close to each other, and are formed into a rectangular tube row to constitute a heat transfer tube row unit serving as a heat exchanger. .
- the primary branch pipe 21 is connected to the inlet ends of all the inner pipes 15 arranged in parallel, and one end of the primary branch pipe 21 is closed by a plug 23.
- Secondary branch pipes 25 are connected to the inlet ends of all the outer pipes 13, one end of each secondary branch pipe 25 is closed by a plug 23, and the above inner pipe 15 passes therethrough.
- a primary collecting pipe 27 is connected to the outlet ends of all the inner pipes 15, and the other end of the primary collecting pipe 27 is closed by a plug 23.
- a secondary collecting pipe 29 is connected to the outlet ends of all the outer pipes 13, the other end of the secondary collecting pipe 29 is closed by a plug 23, and the inner pipe 15 passes therethrough.
- the primary branch pipe 21, the primary collecting pipe 27, the secondary branch pipe 25, and the secondary collecting pipe 29 are straight circular pipes.
- the inner tube 15 is provided with a support member 19 in contact with the inner peripheral surface thereof.
- the support member 19 is made of a coil material having a wire diameter d2 substantially equal to that of the gap support member 17, and has a coil outer diameter D3 equivalent to the inner diameter D6 of the inner tube 15, and the inner peripheral surface of the inner tube 15 It is provided so as to touch the spiral and support it from the inside.
- the outer tube 13 is inserted through an outer tube insertion hole 33 formed in one tube wall of the secondary collecting tube 29 and opens inside the secondary collecting tube 29.
- An inner tube through hole 35 is formed in the other tube wall of the secondary collecting tube 29, and the inner tube 15 inserted through the inner tube through hole 35 is inserted into an inner tube insertion hole 37 formed in the primary branch tube 21. Open inside the primary branch pipe 21.
- the tubes in each of these penetrations are fixed airtight by brazing.
- the brazing can employ a so-called brazing technique in which a brazing material, for example, copper brazing or brass brazing, is placed on the contact surface between the tubes and integrally joined by brazing in a furnace.
- a brazing material for example, copper brazing or brass brazing
- the gap support member 17 and the support member 19 that support the inner tube 15 and the outer tube 13 are also brazed to the inner peripheral surface of the outer tube 13, the outer peripheral surface of the inner tube 15, and the inner peripheral surface of the inner tube 15 in the furnace.
- the materials that are in contact with each other are joined together.
- the gap support member 17 support member 19 is a coil material which is a wire-like member formed in a spiral shape.
- each coil material (17, 19) is in contact with the inner peripheral surface of the outer tube 13, the outer peripheral surface of the inner tube 15, and the inner peripheral surface of the inner tube 15. It becomes a low and joins each other.
- the coil material made of stainless steel may be a coil material that has been pre-quenched and has spring elasticity, or an untreated coil material, that is, a straight wire-shaped material that is deformed into a spiral shape.
- an untreated coil material that can be configured at low cost is preferable.
- it is preferable to use the coil material in the state before the quenching treatment because the heat treatment is performed in the furnace as described above together with the outer tube 13 and the inner tube 15.
- the gap support member 17 and the support member 19 are temporarily welded to the end portions of the inner tube 15 and the outer tube 13 before being put into the furnace, and then the tubes are assembled and put into the furnace.
- the support members 17 and 19 are joined to the inner tube 15 and the outer tube 13, and the outer tube 13, the inner tube 15, the branch tubes 21 and 25, and the collecting tubes 27 and 29, respectively.
- the outer pipe 13 is opened inside the secondary branch pipe 25, and the inner pipe 15 is arranged inside each outer pipe 13.
- the inner pipe 15 led out from the outer pipe 13 by the secondary branch pipe 25 passes through the secondary branch pipe 25 and then opens inside the primary collecting pipe 27.
- the primary collecting pipe 27 forms a heat transfer tube array unit 39 shown in FIG. 2 (a) which has a quadrangular shape on the same plane.
- the inner tube 15 and the outer tube 13 are used as the heat transfer tube 11, and an extremely fine metal round tube is used.
- the area S1 of the primary channel in the inner tube 15 and the secondary channel in the outer tube 13 are used.
- the area S2 and the ratio S1: S2 are set to 1: 2 to 2: 1.
- the inner diameter of the inner tube 15 is 2 to 6 mm, preferably 3 to 5 mm
- the inner diameter of the outer tube 13 is 4 to 10 mm, preferably 5 to 8.5 mm
- the thickness is 0.15 to 0.35 mm. Things are used.
- the area S1 of the primary flow path is about 9.17 mm 2 and the area S2 of the secondary flow path is about 14.70 mm 2 . Is approximately 1: 1.6.
- the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is appropriately changed by changing the diameters of the inner pipe 15 and the outer pipe 13 and the numerical values of the gap support member 17 and the support member 19, respectively.
- the cross-sectional area varies depending on the number of turns and the pitch with respect to the tubes 13 and 15.
- the shape may be changed, and the ratio of flow rates in the inner tube 15 and the outer tube 13 is 1: 1, so that the thermal conductivity can be improved.
- the example of the gap support member 17 is made of a coil material in which the coil inner diameter D1 and the coil outer diameter D2 are constant.
- the present invention is not limited to this.
- the wire diameter d 1 is set smaller than the gap W between the inner tube 15 and the outer tube 13
- the coil inner diameter D 1 in the small diameter portion 43 is set as the outer diameter D 5 of the inner tube 15, and the coil in the large diameter portion 41.
- the outer diameter D2 is the inner diameter D4 of the outer tube 13, and the inner tube 15 is supported in the outer tube 13. According to this heat transfer tube 11, the wire diameter d1 and the gap of the gap support member 17 are interposed at the gap portion W between the outer peripheral surface of the inner tube 15 and the inner peripheral surface of the outer tube 13. Can be secured sufficiently.
- FIG. 6A is a schematic enlarged cross-sectional view of a heat transfer tube according to the present invention
- FIG. 6B is a cross-sectional view taken along line AA of FIG. 7A
- FIG. 7A is a heat transfer tube array unit comprising the heat transfer tubes according to the present invention
- FIG. 8B is a cross-sectional view of a surface perpendicular to the primary branch pipe and including the axis of the inner pipe
- FIG. 8 is a front view of the outer pipe and the inner pipe viewed from the inside of the secondary branch pipe
- FIG. It is a principal part enlarged view of FIG.7 (b).
- the heat transfer tube 11 includes an outer tube 13, an inner tube 15, a gap support member 17, a support member 19, and a heat transfer member 20.
- the outer tube 13 is a straight thin tube, and the inner tube 15 is inserted into the outer tube 13, and both ends are led out from both ends of the outer tube 13.
- the inner tube 15 and the outer tube 13 are coaxial.
- the heat transfer tubes 11 are composed of a plurality of tubes, are arranged in parallel so as to be in the same plane, are arranged close to each other, and form a heat transfer tube array unit 39 that is a rectangular pipe array.
- the primary branch pipe 21 is connected to the inlet ends of all the inner pipes 15 arranged in parallel, and one end of the primary branch pipe 21 is closed by a plug 23.
- a secondary branch pipe 25 is connected to the inlet ends of all the outer pipes 13, one end of the secondary branch pipe 25 is closed by a plug 23, and the above-described inner pipe 15 passes therethrough.
- a primary collecting pipe 27 is connected to the outlet ends of all the inner pipes 15, and the other end of the primary collecting pipe 27 is closed by a plug 23.
- a secondary collecting pipe 29 is connected to the outlet ends of all the outer pipes 13, the other end of the secondary collecting pipe 29 is closed by a plug 23, and the inner pipe 15 passes therethrough.
- the primary branch pipe 21, the primary collecting pipe 27, the secondary branch pipe 25, and the secondary collecting pipe 29 are straight circular pipes.
- the inner tube 15 is provided with a support member 19 in contact with the inner peripheral surface thereof.
- the support member 19 is made of a coil material having a wire diameter d2 substantially equal to that of the gap support member 17, and has a coil outer diameter D3 equivalent to the inner diameter D6 of the inner tube 15, and the inner peripheral surface of the inner tube 15 It is provided so as to touch the spiral and support it from the inside.
- a heat transfer member 20 is provided at the center of the support member 19.
- the heat transfer member 20 is provided over the entire length of the support member 19, and at least a part of the outer periphery is in contact with the support member 19.
- the heat transfer member 20 is a strip 141 that is long in the longitudinal direction of the support member 19 and twisted in a spiral shape.
- the width of the strip 141 is substantially equal to the inner diameter D7 of the support member 19.
- the outer pipe 13 is inserted through an outer pipe insertion hole 33 formed in one of the secondary branch pipe 25 and the secondary collecting pipe 29 and opens inside the secondary branch pipe 25 and the secondary collecting pipe 29.
- An inner pipe through hole 35 is formed in the other pipe wall of the secondary branch pipe 25 and the secondary collecting pipe 29, and the inner pipe 15 inserted through the inner pipe through hole 35 is the primary branch pipe 21 and the primary collecting pipe 27.
- the inner branch insertion hole 37 is formed in the primary branch pipe 21 and the primary collecting pipe 27.
- the tubes in each of these penetrations are fixed airtight by brazing.
- the brazing can employ a so-called brazing technique in which a brazing material, for example, copper brazing or brass brazing, is placed on the contact surface between the tubes and integrally joined by brazing in a furnace. Further, the gap support member 17, the support member 19, and the heat transfer member 20 that support the inner tube 15 and the outer tube 13 are also in the furnace with respect to the outer peripheral surface 32, the outer peripheral surface 30, and the inner peripheral surface 38 of the inner tube. Then, each of the contacting parts is joined with the brazing material.
- a brazing material for example, copper brazing or brass brazing
- the gap support member 17 and the support member 19 are coil members that are spirally formed wire members, such as copper plating, nickel plating, alloy plating thereof, or multilayer plating of copper and nickel.
- the wire diameter is 0.5 to 2 mm.
- the coil material made of stainless steel may be a coil material that has been pre-quenched and has spring elasticity, or an untreated coil material, that is, a straight wire-shaped material that is deformed into a spiral shape. However, an untreated coil material that can be configured at low cost is preferable.
- it is preferable to use the coil material in the state before the quenching treatment because the heat treatment is performed in the furnace as described above together with the outer tube 13 and the inner tube 15.
- the gap support member 17, the support member 19, and the heat transfer member 20 are temporarily fixed by spot welding only the end portions of the inner tube 15 and the outer tube 13 before entering the furnace, and then the inner tube 15 and the outer heat transfer member 20 are fixed.
- the tube 13 can be assembled and placed in a furnace. Thereby, the inner tube 15 and the support member 19, the support member 19 and the heat transfer member 20, the inner tube 15 and the gap support member 17 and the outer tube 13, the primary branch tube 21 and the inner tube 15, the primary collecting tube 27 and the inner tube 15 are obtained.
- the secondary branch pipe 25 and the outer pipe 13, and the secondary collecting pipe 29 and the outer pipe 13 are joined.
- the outer pipe 13 is opened inside the secondary branch pipe 25, and the inner pipe 15 is arranged inside each outer pipe 13.
- the inner pipe 15 led out from the outer pipe 13 by the secondary branch pipe 25 passes through the secondary branch pipe 25 and then opens inside the primary collecting pipe 27.
- the primary collecting pipe 27 forms a heat transfer tube array unit 39 shown in FIG. 7A which is rectangular on the same plane.
- the inner tube 15 and the outer tube 13 are used as the heat transfer tube 11 and extremely thin metal round tubes are used.
- the primary channel cross-sectional area S1 of the inner pipe 15 is (the inner diameter cross-sectional area of the inner pipe 15 ⁇ the cross-sectional area of the support member ⁇ the cross-sectional area of the strip).
- the secondary channel cross-sectional area S2 of the outer tube 13 is (the inner diameter sectional area of the outer tube 13 ⁇ the outer diameter sectional area of the inner tube ⁇ the sectional area of the gap support member).
- the inner tube 15 has an inner diameter of 2 to 6 mm, preferably 3 to 5 mm, and the outer tube 13 has an inner diameter of 4 to 10 mm, preferably 5 to 8.5 mm, and a thickness of 0.15 to 0.35 mm. Is used.
- the ratio of the cross-sectional area S1 of the primary flow path to the cross-sectional area S2 of the secondary flow path is determined by the respective diameter dimensions of the inner tube 15 and the outer tube 13 and the gap support member 17, the support member 19, and the strip plate 141. It is preferable to change the numerical value as appropriate so that the ratio is 1: 1, and the gap support member 17 and the support member 19 made of a coil material have a cross-sectional area depending on the number of turns and the pitch with respect to the inner tube 15 and the outer tube 13. Since it changes, it is good also as changing these shapes, and the improvement of thermal conductivity can be aimed at because the ratio of the flow velocity of the inner tube 15 and the outer tube 13 is set to 1: 1.
- the operation of the heat transfer tube 11 will be described.
- the heat medium flowing through the inner tube 15 flows while contacting the heat transfer member 20 and the support member 19 provided inside the inner tube 15, and conventionally heat that has been in contact only with the inner peripheral surface 38 of the inner tube.
- the contact area of the medium increases.
- the heat medium exchanges heat with the heat transfer member 20 and the support member 19 by heat transfer by contacting the heat transfer member 20 and the support member 19.
- the amount of heat exchanged is transferred to the inner tube 15 by heat conduction, and is exchanged with a heat medium of another system flowing through the gap 31 between the outer tube 13 and the inner tube 15. That is, the amount of heat exchanged in the inner pipe 15 newly contributes to the improvement of the heat exchange efficiency.
- the belt plate 141 which is the heat transfer member 20 is provided in a spiral shape in contact with the support member 20, the support member 19 is disposed in a coil shape in the inner tube 15, and the heat medium flowing through the inner tube 15 is It advances through the inner tube 15 while rotating and meandering.
- the contact area and the contact time with which the heat medium contacts in the inner tube 15 can be increased. Therefore, it is possible to increase the heat exchange rate between the inner pipe 15 and the heat medium flowing through the inner pipe 15 without relatively increasing flow loss with an inexpensive material.
- FIG. 10A is a cross-sectional view of a heat transfer tube provided with a heat transfer member formed by twisting a strip 90 degrees at a predetermined length
- FIG. 10B is a cross-sectional view along line BB in FIG.
- FIG. 11 is a perspective view of the heat transfer member shown in FIG.
- the heat transfer member 20 is formed by twisting a rectangular plate having a predetermined length at both ends, for example, by 180 ° to form a short spiral strip 141, and twisting the predetermined length by 90 °, for example, to connect the end portions to each other.
- a molded configuration may be used.
- the posture can be reversed every 90 degrees to be molded.
- the heat medium is stirred in the inner tube 15, and the contact area can be increased and brought into contact.
- the twist angle of 180 ° and the twist angle of 90 ° of the band plate 141 are not limited to these, and the twist angle may be other angles such as 90 ° and 120 °. Further, the twist angle may be set to other angles such as 45 degrees and 60 degrees to perform molding.
- FIG. 12 is a perspective view of an outer peripheral bulging round bar in which the outer diameter of the round bar is changed to an ellipse and the direction is changed by 90 degrees for each predetermined length.
- FIG. 13A is an outer peripheral bulging round in FIG. (B) is a DD cross-sectional view of (a), (c) is a cross-sectional view of EE of (a), and (d) is a cross-sectional view of FF of (a).
- the heat transfer member 20 can be formed in an outer peripheral bulging round bar 153 having an elliptical portion 155 that is deformed by crushed the circular outer periphery in the radial direction at predetermined intervals in the longitudinal direction of the support member 19.
- the crushed portion bulges outward in the radial direction and becomes an oval part 155.
- the bulging tip side of the oval part 155 is brought into contact with the support member 19.
- the flow path of the heat medium can be stirred and meandered.
- the cross section of the heat transfer tube 11 shown in FIG. When the areas of the primary channel cross-sectional area S1 and the secondary channel cross-sectional area S2 are determined from c, d)), the primary channel cross-sectional area S1 is about 9.5 mm 2 and the secondary channel cross-sectional area S2 is about 12. 1 mm 2 , and these ratios are approximately 1: 1.27.
- the outer peripheral bulging round bar 153 having the oval portion 155 that enables heat conduction with the inner tube 15 can be manufactured relatively inexpensively and easily.
- FIG. 14A is a cross-sectional view of a heat transfer tube provided with different-diameter round bars in which large-diameter portions and small-diameter portions are alternately formed
- FIG. 14B is a GG cross-sectional view of FIG. 14A
- FIG. It is HH sectional drawing of (a).
- the heat transfer member 20 can be formed into a different-diameter round bar 161 in which a circular outer periphery is alternately formed by a small diameter portion 159 and a large diameter portion 157 at predetermined intervals in the longitudinal direction of the support member 19.
- the pitch of the support member 19 is different from the pitch of the large diameter portion 157 and the small diameter portion 159.
- the outer diameter of the small-diameter portion 159 of the different-diameter round bar 161 is 0.3 mm
- the outer diameter of the large-diameter portion 157 is 0.9 mm.
- this heat transfer member 20 when the different-diameter round bar 161 is inserted into the inner tube 15, the heat medium flowing along the different-diameter round bar 161 flows while colliding with the large-diameter portion 157. This collision disturbs the flow of the heat medium, stirs the heat medium flowing in the inner tube 15, and reduces the heat medium that passes without contacting the inner peripheral surface 38, the support member 19, and the heat transfer member 20.
- the heating medium can be easily brought into contact with the inner tube 15, the support member 19, and the heat transfer member 20.
- FIG. 15A is a cross-sectional view of a heat transfer tube provided with a round bar with a constriction in which a large-diameter portion and a small-diameter portion are formed with gentle surfaces
- FIG. 15B is a cross-sectional view taken along II of FIG. ) Is a JJ sectional view of (a).
- the heat transfer member 20 can be formed in a round bar 163 with a constriction in which a large diameter portion 157 and a small diameter portion 159 are formed with gentle surfaces.
- these ratios are S1: S2 in the large-diameter portion 157. ⁇ 1: 1.47, and S1: S2 ⁇ 1: 1.11 at the small diameter portion 159.
- the heat medium flowing in the inner tube 15 is stirred and meandered so that the heat medium can be easily brought into contact with the inner tube 15, the support member 19 and the heat transfer member 20. Further, by forming the round bar material into a shape that is drawn by a predetermined length, the large-diameter portion 157 is substantially equal to the inner diameter of the support member 19 and is supported by contacting a part of the support member 19. Is also possible.
- FIG. 16A is a cross-sectional view of a heat transfer tube provided with a solid bar having a polygonal cross section
- FIG. 16B is a KK cross-sectional view of FIG.
- the heat transfer member 20 can be formed on a solid bar 165 having a polygonal cross section. In the illustrated example, it is formed in a solid bar 165 having a substantially triangular cross section. Since the solid bar 165 is twisted, the ridgeline is not formed parallel to the axis, but is formed in a substantially spiral shape.
- the primary channel cross-sectional area S1 is about 9.5 mm 2 and the secondary channel cross-sectional area S2 is about 12.1 mm 2 . Is approximately 1: 1.27.
- the contact position with the heat medium is set at a plurality of locations by making the cross section triangular in the figure.
- the flow to the support member 19 is formed because the ridge line is substantially spiral.
- the cross-sectional shape is a star shape or the like, and by twisting in the same manner as described above, the contact area with the heat medium can be further increased without reducing the flow path (flow path cross-sectional area).
- the surface area of the heat transfer member 20 can be increased, and the heat exchange rate between the heat medium and the heat transfer member 20 can be increased.
- FIG. 17 is a cross-sectional view of a heat transfer tube provided with a heat transfer member whose ends are formed in a streamline shape in each of the above round bar type shape examples. It is preferable that the heat transfer member 20 of each said shape example of a round bar type forms an edge part in a streamline shape. To reduce the separation and disturbance of the flowing heat medium from the surface of the heat transfer member 20 at the end due to vortices and the like, to smooth the inflow and outflow of the heat medium, and to improve the heat transfer efficiency between the inner pipe 15 of the heat medium. Can do.
- the heat transfer tube 11 of the present embodiment constitutes the heat transfer tube array unit 39 as described above, and may be configured as a single heat exchanger, and as shown in FIG. 18, a plurality of heat transfer tube array units.
- the heat exchanger 49 can be constituted by 39.
- the heat exchanger 49 is configured by stacking a plurality of the above-described heat transfer tube array units 39. In this embodiment, four layers are stacked.
- the other end of the primary branch pipe 21 is connected to the primary inlet header 51
- one end of the secondary branch pipe 25 is connected to the secondary inlet header 55
- the primary collecting pipe 27 is provided in the plurality of heat transfer tube array units 39 arranged in a stacked manner.
- the number of stacking stages is not limited to the four stages shown in the figure, but may be smaller or larger, preferably 4 to 10 stages, each collecting pipe and branch pipe being connected to each header.
- the primary inlet header 51, the secondary inlet header 55, the primary outlet header 53, and the secondary outlet header 57 are closed on one side in the axial direction, and a screw-type pipe joint 59 is fixed on the other side in the axial direction.
- a screw-type pipe joint 59 is fixed on the other side in the axial direction.
- the pipe joint of the primary heat medium supply pipe, the secondary heat medium supply pipe, the primary heat medium recirculation pipe, and the secondary heat medium recirculation pipe from the heat exchange device side expands the diameter of the pipe end.
- the flared portion and a cap nut externally attached to the flared portion, and the female screw of the cap nut is connected to the screw-type fitting 59 in a state in which the tip sheet surface of the screw-type fitting 59 and the flare portion are in close contact with each other.
- the heat exchanger 49 By being screwed onto the male screw, the heat exchanger 49 is detachably attached to the heat exchange device. As described above, the heat exchanger 49 can be easily attached to the heat exchanging device via the screw-in type pipe joint 59 so that the heat exchanger 49 can be easily replaced during maintenance.
- the primary inlet header 51, the secondary inlet header 55, the primary outlet header 53, and the secondary outlet header 57 are closed at the end opposite to the fixed end of the threaded fitting 59 and fixedly supported by, for example, the base plate 61. Is done.
- the primary inlet header 51, the secondary inlet header 55, the primary outlet header 53, and the secondary outlet header 57 can be threadably connected to the threaded pipe joint 59 at the end opposite to the threaded pipe joint 59.
- the pipe joint may be fixed. With such a double-end joint structure, the heat exchanger 49 can be further laminated in a plurality of stages.
- the primary flow that has flowed to the primary inlet header 51 by configuring the heat transfer tube array unit as shown in FIGS. 2 and 7 and the heat exchanger 49 as shown in FIG.
- the heat medium enters the primary branch pipe 21 and flows from the primary branch pipe 21 to each inner pipe 15.
- the primary heat medium flowing through the inner pipe 15 is exchanged with the secondary heat medium, and then enters the primary collecting pipe 27 and exits from the primary outlet header 53 to the outside.
- the secondary heat medium that has flowed to the secondary inlet header 55 enters the secondary branch pipe 25 and flows from the secondary branch pipe 25 to the outer pipe 13.
- the secondary heat medium flowing through the outer pipe 13 is exchanged with the primary heat medium, and then enters the secondary collecting pipe 29 and exits from the secondary outlet header 57 to the outside.
- the heat exchanger 49 having the above configuration will be described.
- the heat medium flowing through the inner pipe 15 flows while contacting the heat transfer member 20 and the support member 19 provided inside the inner pipe 15, and conventionally, only the inner peripheral surface 38 of the inner pipe 15.
- the contact area of the heat medium in the inner tube 15 that has not been in contact increases.
- heat exchange is performed by heat transfer.
- the amount of heat exchanged is transferred to the inner tube 15 by heat conduction, and is exchanged with a heat medium of another system flowing through the gap 31 between the outer tube 13 and the inner tube 15. That is, the amount of heat exchanged with the heat transfer member 20 and the support member 19 newly contributes to the improvement of heat exchange efficiency.
- a plurality of heat transfer tubes 11 including the outer tube 13 and the inner tube 15 are formed in parallel to each other, and are arranged close to each other on the same plane.
- the heat exchanger 49 configured on this plane can be stacked as a single unit in a plurality of stages, and the ground contact area can be reduced while increasing the heat transfer area.
- the heat exchanger tube 11 of this Embodiment can comprise the cylindrical heat exchanger 65 as shown to FIG. 19, 20 besides the heat exchanger 49 mentioned above.
- the heat exchanger 65 is configured by bundling a plurality of heat transfer tubes 11.
- Each heat transfer tube 11 is supported at both ends so as to maintain a predetermined distance from each other, and is accommodated in a cylindrical shell 67.
- a disk-shaped primary partition wall 69 and a secondary partition wall 73 having a large number of support holes 71 and 75 that are equally spaced in the vertical and horizontal directions in a matrix are provided. Both end portions are supported by the partition walls 69 and 73 in a penetrating state.
- the primary partition wall 69 has an inner tube support hole (primary support hole) 71 having a hole diameter equal to the outer diameter of the inner tube 15, and the inner tube 15 passes therethrough.
- the secondary partition wall 73 has an outer tube support hole (secondary support hole) 75 having a hole diameter equivalent to that of the outer tube 13, and the outer tube 13 passes therethrough.
- a primary branching portion 79 is formed on the inlet end side of the inner tube 15 between the primary partition wall 69 and the end wall 77 of the shell 67 in a state where each penetrates, and a primary assembly is formed on the outlet end side of the inner tube 15.
- a portion 81 is formed.
- a secondary branch portion 83 is formed on the inlet end side of the outer tube 13, and a secondary collecting portion 85 is formed on the outlet end side of the outer tube 13.
- the connection between the outer tube 13 and the inner tube 15 of the heat transfer tubes 11 and the partition walls 69 and 73 is also performed by the brazing described above, and the gap disposed in the gap between the outer tube 13 and the inner tube 15.
- the fixing to the support member 17 is the same, and the end portions of the outer tube 13 and the inner tube 15 are opened outside the partition walls 69 and 73.
- a plurality of rectifying plates 87 are provided between the secondary partition walls 73 and 73 in the shell 67. These rectifying plates 87 form a surface that is orthogonal to the longitudinal direction of the heat transfer tube 11, and each has a shape having a notch-shaped passage portion 89 that does not partially contact the inner peripheral surface of the shell 67 in the shell 67, for example, It has a substantially meniscus shape.
- the passage portions 89 of the rectifying plates 87 are provided so as to be alternately positioned in the axial direction in the shell 67, thereby forming a zigzag meandering tertiary flow path in the shell 67.
- each rectifying plate 87 is provided with through holes through which each heat transfer tube 11 penetrates and can support these heat transfer tubes 11, and the above-described through holes and the outer tube 13 of each heat transfer tube 11 also have the above-mentioned. Similar brazing and fixing is preferred.
- a primary inlet header 91 is disposed at the primary branching portion 79, a secondary outlet header 93 is disposed at the secondary collecting portion 85, and an inlet of the tertiary flow path.
- a tertiary inlet header 95 is provided.
- a primary outlet header 97 is disposed in the primary collecting portion 81, a secondary inlet header 99 is disposed in the secondary branch portion 83, and a tertiary outlet header 101 serving as an outlet of the tertiary flow path. Is disposed.
- the primary heat medium that has flowed to the primary inlet header 91 enters the primary branching portion 79 and flows from the primary branching portion 79 to each inner pipe 15.
- the primary heating medium that has flowed through the inner pipe 15 is exchanged with the secondary heating medium, and then enters the primary assembly 81 and exits from the primary outlet header 97.
- the secondary heat medium that has flowed to the secondary inlet header 99 enters the secondary branch portion 83 and flows from the secondary branch portion 83 to the outer tube 13.
- the secondary heat medium that has flowed through the outer tube 13 exchanges heat with the primary heat medium, and then enters the secondary assembly 85 and exits from the secondary outlet header 93 to the outside.
- the tertiary heat medium that has flowed to the tertiary inlet header 95 enters the shell 67, meanders at each rectifying plate 87, and flows around the outer tube 13.
- the tertiary heat medium flowing in the shell 67 is exchanged with the secondary heat medium, and then exits from the tertiary outlet header 101 to the outside.
- the tertiary heat medium may be the same as the primary heat medium.
- the heat transfer tube 11 can exchange heat with the tertiary heat medium in the shell 67, the area S1 of the primary flow path in the inner tube 15 and the secondary flow in the outer tube 13 described above.
- the ratio S1: S2 to the area S2 of the road can be set to 1: 4 to 1: 2, and the gap support member 17 and the inner pipe 15 located in the gap portion between the outer pipe 13 and the inner pipe 15 can be set.
- the wire diameter of the inner support member 19, the shape of the heat transfer member 20, the cross-sectional area, and the like can be appropriately increased or decreased according to these ratios.
- the heat exchange efficiency between the inner tube 15 and the heat medium flowing therethrough can be increased.
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Abstract
Description
また、特許文献1の二重管式熱交換器は、内管の中心が一直線に空間を形成しており、熱媒流の抵抗は小さいが、内管に触れずに流れる熱媒量が多く、熱交換が効率的に行えない問題があった。
本発明の請求項1記載の伝熱管11は、外管13と、
前記外管13に挿入される内管15と、
前記外管13の内周面と前記内管15の外周面との間隙Wに配置され、前記外管13の略全長にわたってらせん状に前記内周面と外周面に接する線材よりなる間隙支持部材17と、
前記内管15の内周面に、該内管15の全長にわたってらせん状に接する線材よりなる支持部材19と、
を具備することを特徴とする。
前記間隙支持部材17は、コイル材よりなり、線径d1が前記間隙Wと略同等とされることを特徴とする。
前記間隙支持部材45は、小径部43と大径部41とが交互に形成されるコイル材よりなり、線径d1が前記間隙Wより小さく、前記小径部43におけるコイル内径D1が前記内管15の外径D5とされ、前記大径部41におけるコイル外径D2が前記外管13の内径D4とされて、前記外管13内に前記内管15が支持されることを特徴とする。
前記外管13に挿入される内管15と、
外管内周面32と内管外周面30との間隙31に配置され、前記外管13の略全長にわたってらせん状に前記外管内周面32と前記内管外周面30に接する線材よりなる間隙支持部材17と、
前記内管内周面38に、前記内管15の全長にわたってらせん状に接する線材よりなる支持部材19と、
前記支持部材19の中心に前記支持部材19の全長にわたって設けられ少なくとも外周の一部分が前記支持部材19に接する伝熱部材20と、
を具備することを特徴とする。
前記伝熱部材20が、
前記支持部材19の長手方向に長く、螺旋状に捻られた帯板141であることを特徴とする。
前記伝熱部材20が、
前記支持部材19の長手方向所定間隔毎に円形外周を潰して変形させた長円部155を有する外周部膨出丸棒153であることを特徴とする。
前記伝熱部材20が、
前記支持部材19の長手方向所定間隔毎に円形外周を小径部159と大径部157とで交互に形成した異径丸棒161であることを特徴とする。
前記伝熱部材20が、
断面多角形状の中実棒165であることを特徴とする。
前記伝熱管11が互いに平行となって複数配置され、
全ての内管入口端を一次分岐管21に接続し且つ全ての内管出口端を一次集合管27に接続して一次流路を構成するとともに、
全ての外管入口端を二次分岐管25に接続し且つ全ての外管出口端を二次集合管29に接続して二次流路を構成してなることを特徴とする。
また、伝熱部材20を備える熱交換器49では、内管15の中を流れる熱媒が、内管15の内側に設けられた伝熱部材20に接触しながら流れ、従来、内管内周面38のみにしか接触していなかった熱媒の接触面積が増大する。熱媒は、伝熱部材20と接触することにより熱伝達によって伝熱部材20と熱交換が行われる。熱交換された熱量は、熱伝導によって内管15に伝わり、外管13と内管15との間隙31を流れる他系統の熱媒と熱交換される。すなわち、伝熱部材20と交換された熱量が、熱交換効率の向上に新たに寄与することとなる。また、この熱交換器49は、外管13及び内管15からなる伝熱管11が、互いに平行に複数で構成され、同一平面上に近接して並べられる。この平面上に構成された熱交換器49は、1つのユニットとして、複数段で積層構成することが可能となり、伝熱面積を広げながら接地面積を小さく構成できる。
前記伝熱管11を複数本で束ね、該伝熱管11の束を円筒形状のシェル67に収容し、前記内管15の入口端同士及び出口端同士をそれぞれ接続して一次流路を構成するとともに、前記外管13の入口端同士及び出口端同士をそれぞれ接続して二次流路を構成し、且つ前記シェル67内を三次流路として構成することを特徴とする。
前記シェル67内には、前記伝熱管11の長手方向に直交する面を有する整流板87が複数設けられ、前記各伝熱管11を支持するとともに、前記三次流路を蛇行させることを特徴とする。
図1は本発明に係る伝熱管の概略拡大断面図を(a)に、A-A断面図を(b)に示した図、図2は本発明に係る伝熱管よりなる熱交換器の伝熱管列ユニットの平面図を(a)に、該平面図におけるB-B線断面図を(b)に示した図、図3は図2に示した伝熱管列ユニットのC-C側断面図、図4は図2(b)に示した断面図の一部拡大断面図である。
本実施の形態に係る伝熱管11は、外管13と、内管15と、間隙支持部材17と、支持部材19とで構成される。
外管13は、真直な細管よりなり、内管15は、外管13に挿入され、この外管13の両端から両端が導出される。そして、内管15と外管13とは同軸心状態とされる。
この伝熱管11は、複数本で構成され同一平面状となるように平行に配列されて互いに近接して並べられ、矩形状の配管列とされて熱交換器となる伝熱管列ユニットを構成する。
図6(a)は本発明に係る伝熱管の概略拡大断面図、(b)は(a)のA-A断面図、図7(a)は本発明に係る伝熱管よりなる伝熱管列ユニットの平面図、(b)は一次分岐管に直交し内管の軸線を含む面の断面図、図8は二次分岐管の内方より見た外管及び内管の正面図、図9は図7(b)の要部拡大図である。
本実施の形態に係る伝熱管11は、外管13と、内管15と、間隙支持部材17と、支持部材19と、伝熱部材20とで構成される。
外管13は、真直な細管よりなり、内管15は、外管13に挿入され、この外管13の両端から両端が導出される。そして、内管15と外管13とは同軸心状態とされる。
この伝熱管11は、複数本で構成され同一平面状となるように平行に配列されて互いに近接して並べられ、矩形状の配管列とされる伝熱管列ユニット39を構成する。
内管15の中を流れる熱媒が、内管15の内側に設けられた伝熱部材20及び支持部材19に接触しながら流れ、従来、内管内周面38のみにしか接触していなかった熱媒の接触面積が増大する。熱媒は、伝熱部材20及び支持部材19と接触することにより熱伝達によって伝熱部材20,支持部材19と熱交換が行われる。熱交換された熱量は、熱伝導によって内管15に伝わり、外管13と内管15との間隙31を流れる他系統の熱媒と熱交換される。すなわち、内管15内で交換された熱量が、熱交換効率の向上に新たに寄与することとなる。
伝熱部材20は、所定長さの長方形板を両端で例えば180°捩じって短尺な螺旋形の帯板141成形し、且つ所定長さ毎に例えば90度ひねって端部同士を連結し成形した構成としてもよい。この場合、帯板141の幅方向中央を通る軸線を挟んで、幅方向の両側から切り込み151を入れておくことで、90度ごとに姿勢を反転させて成形させることができる。この構成によれば、帯板141の外周に位置する支持部材19とともに、熱媒を内管15内で撹拌するようになり接触面積を増やして接触させることができる。なお、上記した帯板141の捩じり角度の180°及びひねり角度の90度は、これらに限定されることはなく、捩じり角度を90°や120°など他の角度としてもよく、またひねり角度を45度や60度などその他の角度に設定し成形しても良い。
伝熱部材20は、支持部材19の長手方向所定間隔毎に円形外周を径方向に潰して変形させた長円部155を有する外周部膨出丸棒153に形成できる。丸棒素材が軸線直交方向から挟まれるように潰されることで、潰された部分が半径方向外側へ膨出し、長円部155となる。この長円部155の膨出先端側が支持部材19に接触するようにする。この潰し方向を例えば90度ずつ交互に変えることで、熱媒の流路を撹拌且つ蛇行させることができる。例えば、内管15を、外径D5=4.4mm,内径D6=4.0mm、外管13を、外径6.6mm,内径D4=6mm、間隙支持部材17を、線径d1=0.8mm、支持部材19を、線径d2=1mmとし、外周部膨出丸棒153の断面積を1.77mm2 として、これら数値に基づき図13に示す伝熱管11の断面(図13(b,c,d))より一次流路断面積S1と二次流路断面積S2の面積を求めると、一次流路断面積S1は約9.5mm2 、二次流路断面積S2は約12.1mm2 となり、これらの比はおよそ1:1.27となる。
この伝熱部材20によれば、内管15と熱伝導を可能とする長円部155を有した外周部膨出丸棒153を、比較的安価に且つ容易に製造できる。
伝熱部材20は、支持部材19の長手方向所定間隔毎に円形外周を小径部159と大径部157とで交互に形成した異径丸棒161に形成できる。支持部材19のピッチと大径部157及び小径部159のピッチは異なる。例えば、内管15を、外径D5=4.0mm,内径D6=3.6mm、外管13を、外径6.6mm,内径D4=6mm、間隙支持部材17と支持部材19を、線径d1=d2=1mmとし、異径丸棒161の小径部159の外径を0.3mm,大径部157の外径を0.9mmとして、これら数値に基づき図14に示す伝熱管11の断面(図14(b,c))より一次流路断面積S1と二次流路断面積S2の面積を求めると、これらの比は、大径部157においてS1:S2≒1:1.7、小径部159においてS1:S2≒1:1.6となる。
伝熱部材20は、大径部157と小径部159とがなだらかな面で形成される括れ付き丸棒163に形成できる。例えば、内管15を、外径D5=4.4mm,内径D6=4.0mm、外管13を、外径6.6mm,内径D4=6mm、間隙支持部材17を、線径d1=0.8mm、支持部材19を、線径d2=1mmとし、括れ付き丸棒163の小径部159の外径を0.76mm,大径部157の外径を2.0mmとして、これら数値に基づき図15に示す伝熱管11の断面(図15(b,c))より一次流路断面積S1と二次流路断面積S2の面積を求めると、これらの比は、大径部157においてS1:S2≒1:1.47、小径部159においてS1:S2≒1:1.11となる。
伝熱部材20は、断面多角形状の中実棒165に形成できる。図例では、断面略三角形状の中実棒165に形成される。中実棒165は、ひねっていることで、稜線が軸線に平行ではなく略螺旋状に形成される。
例えば、内管15を、外径D5=4.4mm,内径D6=4.0mm、外管13を、外径6.6mm,内径D4=6mm、間隙支持部材17を、線径d1=0.8mm、支持部材19を、線径d2=1mmとし、中実棒165の断面積を1.8mm2 として、これら数値に基づき図16に示す伝熱管11の断面(図16(b))より一次流路断面積S1と二次流路断面積S2の面積を求めると、一次流路断面積S1は約9.5mm2 、二次流路断面積S2は約12.1mm2 となり、これらの比はおよそ1:1.27となる。
丸棒タイプの上記各形状例の伝熱部材20は、端部を流線形状に形成することが好ましい。端部における流れる熱媒の伝熱部材20表面からの渦等による剥離や乱れを少なくして、熱媒の流入及び流出をスムースとし、熱媒の内管15内との熱伝達効率を高めることができる。
この熱交換器49は、上記した伝熱管列ユニット39を複数段積層して構成される。この実施形態では、4段に積層される。積層配置された複数の伝熱管列ユニット39は、一次分岐管21の他端が一次入口ヘッダ51に接続され、二次分岐管25の一端が二次入口ヘッダ55に接続され、一次集合管27の一端が一次出口ヘッダ53に接続され、二次集合管29の一端が二次出口ヘッダ57に接続される。積層段数は図例の4段に限定されるものではなく、これより少なくても多くてもよく、好ましくは4~10段で構成され、それぞれの集合管及び分岐管が、各ヘッダに接続される。
熱交換器49では、内管15の中を流れる熱媒が、内管15の内側に設けられた伝熱部材20及び支持部材19に接触しながら流れ、従来、内管内周面38のみにしか接触していなかった内管15内における熱媒の接触面積が増大する。熱媒は、支持部材19,伝熱部材20と接触することにより熱伝達によって熱交換が行われる。熱交換された熱量は、熱伝導によって内管15に伝わり、外管13と内管15との間隙31を流れる他系統の熱媒と熱交換される。すなわち、伝熱部材20,支持部材19と交換された熱量が、熱交換効率の向上に新たに寄与することとなる。また、この熱交換器49は、外管13及び内管15からなる伝熱管11が、互いに平行に複数で構成され、同一平面上に近接して並べられる。この平面上に構成された熱交換器49は、1つのユニットとして、複数段で積層構成することが可能となり、伝熱面積を広げながら接地面積を小さく構成できる。
この熱交換器65は、この伝熱管11を複数本で束にして構成される。各伝熱管11は、互いに所定間隔を保つように両端が支持され、円筒状のシェル67内に収容されている。本実施の形態では、図19に示すように、マトリクス状に縦横方向で等間隔となる多数の支持孔71,75を有した円板形状の一次隔壁69と二次隔壁73とを備え、これら隔壁69,73にて両端部分が貫通状態で支持される。一次隔壁69は、内管15の外径と同等の孔径とされる内管支持孔(一次支持孔)71を有し、内管15が貫通する。二次隔壁73は、外管13と同等の孔径とされる外管支持孔(二次支持孔)75を有し、外管13が貫通する。それぞれが貫通した状態で、一次隔壁69とシェル67の端部壁77との間では内管15の入口端側には一次分岐部79が形成され、内管15の出口端側には一次集合部81が形成される。また、一次隔壁69と二次隔壁73との間では外管13の入口端側には二次分岐部83が形成され、外管13の出口端側には二次集合部85が形成される。なお、これら伝熱管11の外管13及び内管15と各隔壁69,73との接続においても、上述したロウ付けにて行われ、外管13と内管15との間隙に配置される間隙支持部材17との固定も同様であり、各隔壁69,73の外側に外管13,内管15の端部が開口することとなる。
13…外管
15…内管
17,45…間隙支持部材
19…支持部材
20…伝熱部材
21…一次分岐管
25…二次分岐管
27…一次集合管
29…二次集合管
30…内管外周面
31…間隙
32…外管内周面
38…内管内周面
41…大径部
43…小径部
49,65…熱交換器
67…シェル
87…整流板
141…帯板
153…外周部膨出丸棒
155…長円部
157…大径部
159…小径部
161…異径丸棒
165…中実棒
d1…間隙支持部材の線径
D1…コイル内径
D2…コイル外径
D4…外管の内径
D5…内管の外径
W…間隙
Claims (11)
- 外管と、
前記外管に挿入される内管と、
前記外管の内周面と前記内管の外周面との間隙に配置され、前記外管の略全長にわたってらせん状に前記内周面と外周面に接する線材よりなる間隙支持部材と、
前記内管の内周面に、該内管の全長にわたってらせん状に接する線材よりなる支持部材と、
を具備することを特徴とする伝熱管。 - 前記間隙支持部材は、コイル材よりなり、線径が前記間隙と略同等とされることを特徴とする請求項1記載の伝熱管。
- 前記間隙支持部材は、小径部と大径部とが交互に形成されるコイル材よりなり、線径が前記間隙より小さく、前記小径部におけるコイル内径が前記内管の外径とされ、前記大径部におけるコイル外径が前記外管の内径とされて、前記外管内に前記内管が支持されることを特徴とする請求項1記載の伝熱管。
- 外管と、
前記外管に挿入される内管と、
外管内周面と内管外周面との間隙に配置され、前記外管の略全長にわたってらせん状に前記外管内周面と前記内管外周面に接する線材よりなる間隙支持部材と、
前記内管内周面に、前記内管の全長にわたってらせん状に接する線材よりなる支持部材と、
前記支持部材の中心に前記支持部材の全長にわたって設けられ少なくとも外周の一部分が前記支持部材に接する伝熱部材と、
を具備することを特徴とする伝熱管。 - 請求項4記載の伝熱管であって、
前記伝熱部材が、
前記支持部材の長手方向に長く、螺旋状に捻られた帯板であることを特徴とする伝熱管。 - 請求項4記載の伝熱管であって、
前記伝熱部材が、
前記支持部材の長手方向所定間隔毎に円形外周を潰して変形させた長円部を有する外周部膨出丸棒であることを特徴とする伝熱管。 - 請求項4記載の伝熱管であって、
前記伝熱部材が、
前記支持部材の長手方向所定間隔毎に円形外周を小径部と大径部とで交互に形成した異径丸棒であることを特徴とする伝熱管。 - 請求項4記載の伝熱管であって、
前記伝熱部材が、
断面多角形状の中実棒であることを特徴とする伝熱管。 - 請求項1~8のいずれか1つに記載の伝熱管を用いた熱交換器であって、
前記伝熱管が互いに平行となって複数配置され、
全ての内管入口端を一次分岐管に接続し且つ全ての内管出口端を一次集合管に接続して一次流路を構成するとともに、
全ての外管入口端を二次分岐管に接続し且つ全ての外管出口端を二次集合管に接続して二次流路を構成してなることを特徴とする熱交換器。 - 請求項1~8のいずれか1つに記載の伝熱管を用いた熱交換器であって、
前記伝熱管を複数本で束ね、該伝熱管の束を円筒形状のシェルに収容し、前記内管の入口端同士及び出口端同士をそれぞれ接続して一次流路を構成するとともに、前記外管の入口端同士及び出口端同士をそれぞれ接続して二次流路を構成し、且つ前記シェル内を三次流路として構成することを特徴とする熱交換器。 - 前記シェル内には、前記伝熱管の長手方向に直交する面を有する整流板が複数設けられ、前記各伝熱管を支持するとともに、前記三次流路を蛇行させることを特徴とする請求項10記載の熱交換器。
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Also Published As
Publication number | Publication date |
---|---|
KR20150006823A (ko) | 2015-01-19 |
CN203323601U (zh) | 2013-12-04 |
US20150300746A1 (en) | 2015-10-22 |
TW201346206A (zh) | 2013-11-16 |
JPWO2013150818A1 (ja) | 2015-12-17 |
CN103363820A (zh) | 2013-10-23 |
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