WO2015107970A1 - Heat transfer tube for heat exchanger and heat exchanger - Google Patents

Heat transfer tube for heat exchanger and heat exchanger Download PDF

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Publication number
WO2015107970A1
WO2015107970A1 PCT/JP2015/050327 JP2015050327W WO2015107970A1 WO 2015107970 A1 WO2015107970 A1 WO 2015107970A1 JP 2015050327 W JP2015050327 W JP 2015050327W WO 2015107970 A1 WO2015107970 A1 WO 2015107970A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
tube
flow path
cross
exchanger tube
Prior art date
Application number
PCT/JP2015/050327
Other languages
French (fr)
Japanese (ja)
Inventor
滝波重明
安田健太郎
植野浩治
仲田裕一
Original Assignee
シーアイ化成株式会社
株式会社仲田製作所
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Application filed by シーアイ化成株式会社, 株式会社仲田製作所 filed Critical シーアイ化成株式会社
Publication of WO2015107970A1 publication Critical patent/WO2015107970A1/en

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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
    • F28D7/14—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 both tubes being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—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
    • 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

Definitions

  • the present invention relates to a double-tube heat exchanger tube having an outer tube and an inner tube and a heat exchanger using the same.
  • a heat exchanger tube for heat exchangers As a heat exchanger tube for heat exchangers, a double tube type heat is exchanged between a fluid passing through the inner tube and a fluid flowing between the inner tube and the outer tube through the inner tube.
  • a heat exchanger tube for an exchanger is known (see, for example, Patent Document 1).
  • a heat transfer promoting body that spirally partitions the inner flow path of the outer tube is interposed between the inner tube and the outer tube.
  • a double wound spring having a space between the inner and outer tubes as two spiral channels or a single spring having a space between the inner and outer tubes as one spiral channel. Can be used.
  • This increases the flow path length of the flow path between the inner and outer pipes, and increases the flow velocity and turbulence of the fluid flowing through the flow path. As a result, heat transfer from the fluid flowing in the inner pipe to the fluid flowing between the inner and outer pipes is promoted, and the performance per unit length can be improved.
  • the above-described double tube heat exchanger is configured by inserting one inner tube inside one outer tube.
  • the first flow path constituted by the inner side of the outer pipe and the outer side of the inner pipe and the second flow path constituted by the inner side of the inner pipe are set to the first flow path cross-sectional area ratio. It is difficult to increase the heat exchange area between the flow path and the second flow path with an easy manufacturing method.
  • the conventional double-pipe heat exchanger heat exchanger tube for heat exchanger
  • the tube length becomes long so it is difficult to make the heat exchanger compact.
  • the present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger tube for a heat exchanger that has a high heat exchange rate, is easy to manufacture, and can be configured compactly, and a heat exchanger using the heat exchanger tube. There is.
  • Cross-sectional area S2 It is characterized by comprising.
  • the outer tube 13 has a first coil 17 that is partially fixed to the inner peripheral surface 21 of the outer tube, and each of the inner tubes 15 is fixed to the inner peripheral surface 23 of the inner tube.
  • Two coils 19 are provided.
  • the 1st coil 17 and the 2nd coil 19 play a role which disturbs fluid, and promotes heat transfer.
  • a plurality of inner pipes 15 are inserted inside the first coil 17.
  • this adjustment can be performed by changing the number of inner tubes 15 and the diameter size of the inner tubes 15.
  • the flow path cross-sectional area S1 of the first flow path 25 formed by the inner side of the outer pipe 13 and the outer side of the inner pipe 15 and the flow path cross-sectional area S2 of the second flow path 27 of the inner pipe 15 are 1: 2. It is configured to be ⁇ 2: 1. Thereby, the shortage of the channel cross-sectional area of the first channel 25 due to S1 / S2 being 1/2 or less does not occur. In addition, there is no shortage of the channel cross-sectional area of the second channel 27 where S1 / S2 is 2/1 or more.
  • the heat exchanger tube 11 for a heat exchanger according to claim 2 of the present invention is the heat exchanger tube 11 for a heat exchanger according to claim 1, A core material is inserted along the inner pipe 15 at an arbitrary position of the first flow path 25.
  • the fluid flowing through the first flow path 25 is easily dispersed. That is, the movement of the fluid flowing in the radial inner side and the radial outer side in the channel cross-sectional area of the first channel 25 is promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased.
  • the fluid flowing through the first flow path 25 at the portion where the core material is disposed can be eliminated, the flow path cross-sectional area of the first flow path 25 can be reduced and adjusted.
  • the heat exchanger tube 11 for a heat exchanger according to claim 3 of the present invention is the heat exchanger tube 11 for a heat exchanger according to claim 2,
  • the core material is a solid bar 29.
  • the fluid flowing through the first flow path 25 can be effectively removed by the volume of the solid rod 29.
  • the heat exchanger tube 11 for heat exchanger according to claim 4 of the present invention is the heat exchanger tube 11 for heat exchanger according to claim 2,
  • the core material is a coil member.
  • the heat exchanger tube 11 for heat exchanger it is possible to disturb or stir the flow of the fluid flowing in the vicinity of the coil member of the first flow path 25. By this stirring, the movement of the fluid flowing through the radially inner side and the radially outer side in the channel cross-sectional area of the first channel 25 is more effectively promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased.
  • the heat exchanger tube for a heat exchanger according to claim 5 of the present invention is the heat exchanger tube for a heat exchanger according to claim 2,
  • the core material is a strip-like member 47 formed in a spiral shape.
  • the flow of the fluid flowing through the first flow path 25 can be disturbed or agitated by forming the strip plate member 47 in a spiral shape.
  • stirring the movement of the fluid flowing through the radially inner side and the radially outer side in the channel cross-sectional area of the first channel 25 is more effectively promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased.
  • the heat exchanger tube 11 for heat exchanger according to claim 6 of the present invention is the heat exchanger tube for heat exchanger according to any one of claims 1, 2, 3, 4, and 5, A bent portion is provided.
  • the heat exchanger tube 11 for heat exchanger as a tube shape, it is possible to have a configuration in which a middle portion or the like has a bent portion at an arbitrary angle, and when the bent portion is formed at the position of the bent portion, The outer tube and the inner tube are not crushed by having the first coil and the second coil. And by setting it as the shape provided with this bending part, the flow path inlet / outlet of both ends can be comprised in arbitrary directions, and the whole magnitude
  • the heat exchanger tube 11 for a heat exchanger according to claim 7 of the present invention is the heat exchanger tube 11 for a heat exchanger according to any one of claims 1, 2, 3, 4, and 5, It is characterized by comprising a pair of first bent portion 31 and second bent portion 33 which are bent in the opposite direction with the same radius and the same bending angle on the same plane.
  • the length variation of the bent portion of each tube can be offset by making the tube shape into an S shape that is bent in the opposite direction with the same radius and the same bending angle. This makes it possible to align all the straight lengths before the formation of the bend, and after forming the bend into an S-shape, it is possible to align the ends of the tubes.
  • a heat exchanger according to an eighth aspect of the present invention includes the heat exchanger tube for a heat exchanger according to any one of the first to seventh aspects.
  • this heat exchanger consists of a plurality of inner tubes inserted inside one outer tube and a heat exchanger tube for a heat exchanger having a coil disposed in each flow path,
  • the heat exchanger has an improved heat exchange rate, and can be configured compactly.
  • the inner tube is composed of a plurality of coils and the coil is disposed in each flow path, it has a high heat exchange rate and is easy to manufacture. Can be configured compactly.
  • the heat transfer rate to the fluid flowing through the first flow path can be increased, and the flow path between the first flow path and the second flow path.
  • the cross-sectional area ratio can be easily adjusted.
  • the flow path cross-sectional area of the first flow path is effectively reduced by the core made of the solid rod arranged in the first flow path. That is, reduction adjustment can be performed.
  • the first flow path is reduced while the flow path cross-sectional area of the first flow path is reduced by the coil member disposed in the first flow path.
  • the flowing fluid can be agitated to improve the heat exchange rate.
  • the heat exchanger tube for heat exchanger while reducing the flow passage cross-sectional area of the first flow path by the spiral strip-shaped member disposed in the first flow path, The fluid flowing through the first flow path can be agitated to improve the heat exchange rate.
  • the heat exchanger tube for a heat exchanger according to claim 6 of the present invention, by providing the bent portion, the heat exchanger tube can be configured in an arbitrary shape and can be made compact.
  • the bent portions are formed in an S shape with the same radius and the same bending angle as opposite directions, the end portions of the inner and outer tubes are faced. For one thing, it is possible to easily manufacture a bendable structure that can be made compact.
  • a plurality of inner pipes are inserted inside one outer pipe, and a coil is provided in each flow path. Therefore, a heat exchanger having an improved heat exchange rate can be obtained. Moreover, since the length of a heat exchanger tube can be comprised from this and a heat exchanger tube can also be bent, it can be comprised compactly as a heat exchanger.
  • FIG. 4 is a view taken along arrow AA in FIG. 3.
  • FIG. 4 is a sectional view taken along line BB in FIG. 3.
  • FIG. 4 is a sectional view taken along the line CC of FIG. 3.
  • FIG. 10 is a cross-sectional view in the direction perpendicular to the axis of the heat exchanger tube for heat exchanger shown in FIG. 9.
  • FIG. 1 is a side view of a principal part of a heat exchanger tube for heat exchanger according to an embodiment of the present invention, a part of which is cut away
  • FIG. 2 is a cross-sectional view of the heat exchanger tube for heat exchanger shown in FIG. 4 is a plan view of the heat exchanger tube for heat exchanger formed in an S-shape
  • FIG. 4 is a view taken along the line AA in FIG. 3
  • FIG. 5 is a cross-sectional view along BB in FIG. 3
  • FIG. It is sectional drawing.
  • the heat exchanger tube 11 for a heat exchanger includes an outer tube 13, an inner tube 15, a first coil 17, a second coil 19, a channel cross-sectional area S1, and a channel cross-sectional area S2.
  • the outer tube 13 is formed in a circular shape in the cross section orthogonal to the axis.
  • copper or stainless steel can be used as the material of the outer tube 13 and the inner tube 15.
  • other metals and alloys may be used as long as they have the same degree of thermal conductivity and heat resistance temperature, corrosion resistance, and strength are ensured.
  • the outer tube 13 and the inner tube 15 may be seamless seamless tubes or electric sewing tubes.
  • the inner tube 15 includes a plurality of inner tubes 15 in the present embodiment.
  • the inner tubes 15 are inserted into the outer tube 13 in parallel with each other in the same direction. Equally arranged. That is, the four inner pipes 15 are arranged so that the distances from the axis of the outer pipe 13 to the respective axes are substantially equal. Moreover, it is preferable that the four inner pipes 15 are arranged so that the lines connecting the respective axes are in a regular polygonal shape, for example, a square shape in a cross-sectional view, so that heat exchange is performed evenly. Furthermore, it is preferable that the outer peripheral surfaces of the four inner pipes 15 are separated from each other. Thereby, the fluid can be made to flow evenly inside the outer tube 13. Note that “the mutual distance between the axes is substantially equal” means that the longest distance between the axes is within a range of 100 to 120% of the shortest distance between the axes.
  • the number of inner tubes 15 is not limited to four, and may be two, three, or five or more.
  • the first coil 17 is at least partially fixed to the inner peripheral surface 21 of the outer tube.
  • a plurality of inner pipes 15 are inserted inside the first coil 17.
  • the four inner pipes 15 may be arranged so as to be in contact with the first coil 17.
  • the second coil 19 is at least partially fixed to the inner peripheral surface 23 of each inner tube.
  • each second coil 19 is formed in the same shape.
  • the 1st coil 17 and the 2nd coil 19 consist of a metal wire with the same favorable electroconductivity as the above, and become coil spring shape by being wound spirally.
  • the first coil 17 and the second coil 19 are fixed to the inner peripheral surface 21 of the outer tube and the inner peripheral surface 23 of the inner tube by brazing, for example.
  • the first flow path 25 constituted by the inner side of the outer pipe 13 and the outer side of the inner pipe 15 is assumed to be a flow path cross-sectional area S1.
  • the second flow path 27 configured by summing the flow path cross-sectional areas of the respective inner pipes 15 is defined as a flow path cross-sectional area S2.
  • a core material is inserted along the inner pipe 15 at an arbitrary position of the first flow path 25.
  • the core material can be used as a means for adjusting the channel cross-sectional area ratio between the channel cross-sectional area S1 and the channel cross-sectional area S2.
  • a solid bar 29 may be coaxially disposed at the center of the outer tube 13. In that case, it is preferable that the solid rod 29 and the outer peripheral surface of the inner tube 15 are separated from each other so that the fluid flowing through the first flow path 25 flows evenly in the outer tube 13.
  • the core material is not limited to the solid rod 29, and may be a coil member, a strip plate member 47, or the like as long as the fluid dispersion effect and the flow path cross-sectional area ratio adjustment effect can be obtained. .
  • the position of the core material may be shifted from the axis of the outer tube 13 as long as the fluid dispersion effect and the flow path cross-sectional area ratio adjustment effect can be obtained.
  • the core material may be disposed in a substantially triangular portion formed by the outer tube 13 and the two inner tubes 15 adjacent to each other as long as the above-described effect can be obtained. A total of four things may be arrange
  • the outer tube 13 has an outer diameter of 10 mm, an inner diameter of 8.4 mm, and a thickness of 0.8 mm.
  • the inner tube 15 has an outer diameter of 3 mm, an inner diameter of 2.5 mm, and a thickness of 0.2 mm.
  • the first coil 17 has a wire diameter of 0.3 mm, an inner diameter of 7.5 mm, an outer diameter of 8.1 mm, and the second coil 19 has a wire diameter of 0.3 mm and an inner diameter of 1.7 mm.
  • the outer diameter as 2.3 mm furthermore, the core, when the 1mm diameter, these numerical values, for example, flow path cross-sectional area S1 is 15.1 mm 2, flow path cross-sectional area S2 is a by 9.08 2 Calculated.
  • the heat exchanger heat transfer tube 11 has a pair of first bent portion 31 and second bent portion that are bent in the same direction and at the same radius and the same bending angle R, for example, 180 °.
  • the portion 33 can be formed into an S shape.
  • a T-shaped joint 35 is connected to both ends of the outer tube 13.
  • Each T-shaped joint 35 is connected to a socket 37 at the end opposite to the outer tube 13.
  • the socket 37 closes the first flow path 25 opened to the inside of the T-shaped joint 35 and leads the inner tube 15 to the outside.
  • Each inner pipe 15 led out to the outside is inserted into another socket 39 with its outer periphery sealed in a watertight manner.
  • the second flow path 27 of each inner tube 15 is opened inside the socket 39.
  • the connection pipe 41 is connected to the remaining connection portion of the T-shaped joint 35 in which the first flow path 25 is opened.
  • the first flow path 25 is connected to the connection pipe 41 via the T-shaped joint 35.
  • FIG. 7 is a cross-sectional view of a heat exchanger tube 43 for a heat exchanger according to a modification in which the core material is omitted
  • FIG. 8 is a cross-sectional view of the heat exchanger tube 43 for heat exchanger shown in FIG. 7
  • FIG. 9 is a core material
  • FIG. 10 is a cross-sectional view of the heat exchanger tube 45 for heat exchanger shown in FIG. 9 in a direction orthogonal to the axis line.
  • the said heat exchanger tube 11 for heat exchangers may abbreviate
  • the core material is a coil member
  • the number of turns, the wire diameter, and the like may be changed according to the flow path cross-sectional area ratio.
  • the shape of the core material may be configured as a strip-like member 47 formed in a spiral shape instead of the solid rod 29 described above.
  • the second coil 19 inserted into each of the inner tubes 15 may be different in shape, number of turns, wire diameter, etc. for each inserted inner tube 15.
  • the outer tube 13 has a first coil 17 that fixes a part to the inner peripheral surface 21 of the outer tube, and each inner tube 15 fixes a second part to the inner peripheral surface 23 of the inner tube. It has a coil 19.
  • the 1st coil 17 and the 2nd coil 19 play the role which disturbs the fluid which flows through each pipe, and the role which promotes heat transfer.
  • a plurality of inner pipes 15 are inserted inside the first coil 17. This makes it easier to adjust the heat exchange area with the fluid flowing through the first flow path 25 and to adjust the cross-sectional area of the flow path in the second flow path 27 than when there is only one inner tube 15. It is obtained by an easy manufacturing method. More specifically, this adjustment can be performed by changing the number of the inner tubes 15, the diameter size of the inner tubes 15, and the thickness of the inner tubes 15.
  • the flow path cross-sectional area S1 of the first flow path 25 formed by the inner side of the outer pipe 13 and the outer side of the inner pipe 15 and the flow path cross-sectional area S2 of the second flow path 27 of the inner pipe 15 are 1: 2. It is configured to be ⁇ 2: 1. Thereby, the shortage of the channel cross-sectional area of the first channel 25 due to S1 / S2 being 1/2 or less does not occur. Further, the shortage of the channel cross-sectional area of the second channel 27 in which S1 / S2 is 2/1 or more does not occur.
  • the flow passage cross-sectional area ratio between the first flow passage 25 and the second flow passage 27 can be easily adjusted, and the flow passage cross-sectional area ratio is brought closer to a more preferable ratio. Is easily possible.
  • the fluid flowing through the first flow path 25 is easily dispersed by providing the first flow path 25 with the solid rod 29 and the strip plate member 47 as the core material. That is, the movement of the fluid flowing in the radial inner side and the radial outer side in the channel cross-sectional area of the first channel 25 is promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased.
  • the flow path cross-sectional area of the first flow path 25 can be reduced and adjusted. Thereby, the heat transfer rate to the fluid flowing through the first flow path 25 can be increased, and the flow path cross-sectional area ratio between the first flow path 25 and the second flow path 27 can be easily adjusted.
  • the core material is the solid rod 29
  • the fluid flowing through the first flow path 25 can be eliminated by the volume of the solid rod 29.
  • the channel cross-sectional area of the first channel 25 can be effectively reduced and reduced and adjusted.
  • the thickness of the inner tube 15 can be increased or decreased, and the flow path cross-sectional area ratio can be adjusted.
  • the core member is the coil member or the strip plate member 47
  • the flow of the fluid flowing in the vicinity of the coil member or the strip plate member 47 of the first flow path 25 can be disturbed or agitated.
  • the movement of the fluid flowing through the radially inner side and the radially outer side in the channel cross-sectional area of the first channel 25 is more effectively promoted, and a temperature gradient is easily obtained.
  • the heat exchange rate is increased.
  • the length variation of the bent portion of each tube can be offset by making the tube shape into an S shape that is bent in the opposite directions with the same radius and the same bending angle.
  • the length of each straight tube before being bent into the S shape can be configured to be the same, and after the bending into the S shape, the ends of the tubes can be made flush.
  • the heat exchanger tubes 11, 43, 45 for the heat exchanger of the above-described embodiment are configured by a plurality, and are arranged in parallel so as to be in the same plane and arranged close to each other, or a plurality of the tubes are bundled.
  • the heat transfer tube array unit is configured, and this is configured as a heat exchanger (not shown).
  • a heat exchanger can be configured by stacking a plurality of units as a unit.
  • the plurality of heat transfer tube array units arranged in a stack are connected to, for example, the first flow paths of the heat transfer tubes for the heat exchangers and the second flow paths are connected to the primary inlet header and the primary outlet, respectively. It is connected to each of the header, secondary inlet header, and secondary outlet header.
  • 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 exchanger side are connected to the primary inlet.
  • the primary heat medium that has flowed to the header flows to the inner tube 15, for example.
  • the primary heating medium that has flowed through the inner pipe 15 is exchanged with the secondary heating medium, and then exits from the primary outlet header.
  • the secondary heat medium that has flowed to the secondary inlet header flows to the outer tube 13.
  • the secondary heat medium that has flowed through the outer tube 13 is exchanged with the primary heat medium and then exits from the secondary outlet header.
  • the heat exchanger having the above configuration, the heat medium flowing through the inner tube 15 is disturbed by the second coil 19 provided inside the inner tube 15 and flows while being stirred. In comparison, heat transfer is promoted and heat exchange is performed. Then, heat exchange is performed with a heat medium of another system that flows through the gap between the outer tube 13 and the inner tube 15.
  • the heat exchanger includes a plurality of heat transfer tubes 11 each including an outer tube 13 and an inner tube 15 that are arranged in parallel to each other and are arranged close to each other on the same plane.
  • the tube length can be shortened because it can be easily manufactured and the heat exchange rate is improved, and the heat using the heat exchanger tube for heat exchanger is increased.
  • the pipe length can be shortened and the structure can be made compact.

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

Abstract

[Problem] To provide a heat transfer tube for a heat exchanger, which enables the heat exchanger to have a compact construction. [Solution] A heat transfer tube (11) for a heat exchanger is provided with: an outer tube (13); multiple inner tubes (15) inserted through the outer tube (13) so that the axes of the inner tubes are arranged with an equal distance from one to the other in a cross section orthogonal to the axes; a first coil (17) having at least a portion thereof fixed on an inner circumferential surface (21) of the outer tube, said multiple inner tubes (15) being inserted through the first coil (17); second coils (19) each having at least a portion thereof fixed on an inner circumferential surface (23) of each inner tube; a flow path cross-section area (S1) of a first flow path (25) defined by the inside of the outer tube (13) and the outsides of the inner tubes (15); and a flow path cross section area (S2) of second flow paths (27), defined by a total area of flow path cross sections of the inner tubes (15) and having a ratio with the flow path cross section (S1) such that S1:S2 = 1:2 to 2:1.

Description

熱交換器用伝熱管及び熱交換器Heat exchanger tube for heat exchanger and heat exchanger
　本発明は、外管と内管とを有する二重管式の熱交換器用伝熱管とそれを用いた熱交換器に関する。 The present invention relates to a double-tube heat exchanger tube having an outer tube and an inner tube and a heat exchanger using the same.
　熱交換器用伝熱管として、外管内に内管を挿通し、内管内を流通する流体と、内管と外管との間を流通する流体との間で熱交換を行う二重管式の熱交換器用伝熱管が知られている（例えば特許文献１参照）。同文献に開示される二重管式熱交換器は、内管と外管との間に、外管の内側流路を螺旋状に仕切る伝熱促進体を介設している。伝熱促進体としては、内外管の間の空間を２本の螺旋状流路とする２重巻のスプリングあるいは内外管の間の空間を１本の螺旋状流路とする１重巻のスプリングを用いることが可能とされている。
　これにより、内外管の間の流路の流路長を増大させるとともに、この流路を流れる流体の流速及び乱流化を増加させる。その結果、内管内を流れる流体から内外管の間を流れる流体への伝熱が促進され、単位長さ当たりの性能向上が可能とされている。 As a heat exchanger tube for heat exchangers, a double tube type heat is exchanged between a fluid passing through the inner tube and a fluid flowing between the inner tube and the outer tube through the inner tube. A heat exchanger tube for an exchanger is known (see, for example, Patent Document 1). In the double-tube heat exchanger disclosed in the same document, a heat transfer promoting body that spirally partitions the inner flow path of the outer tube is interposed between the inner tube and the outer tube. As a heat transfer promoting body, a double wound spring having a space between the inner and outer tubes as two spiral channels or a single spring having a space between the inner and outer tubes as one spiral channel. Can be used.
This increases the flow path length of the flow path between the inner and outer pipes, and increases the flow velocity and turbulence of the fluid flowing through the flow path. As a result, heat transfer from the fluid flowing in the inner pipe to the fluid flowing between the inner and outer pipes is promoted, and the performance per unit length can be improved.
特開２００１－２０１２７５号公報（段落番号００３２、図７、図８参照）Japanese Patent Laid-Open No. 2001-201275 (see paragraph number 0032, FIG. 7 and FIG. 8)
　しかしながら、上記の二重管式熱交換器は、１本の外管の内側に、１本の内管を挿通して構成されている。このため、外管の内側と内管の外側とで構成される第１流路と、内管の内側に構成される第２流路とを、最適な流路断面積比としながら、第１流路と第２流路の熱交換面積を容易な製造方法で増やすことが難しい。その結果、従来の二重管式熱交換器（熱交換器用伝熱管）は、熱交換率を向上させにくく、管長が長くなることから、熱交換器のコンパクト化が困難であった。 However, the above-described double tube heat exchanger is configured by inserting one inner tube inside one outer tube. For this reason, the first flow path constituted by the inner side of the outer pipe and the outer side of the inner pipe and the second flow path constituted by the inner side of the inner pipe are set to the first flow path cross-sectional area ratio. It is difficult to increase the heat exchange area between the flow path and the second flow path with an easy manufacturing method. As a result, the conventional double-pipe heat exchanger (heat exchanger tube for heat exchanger) is difficult to improve the heat exchange rate and the tube length becomes long, so it is difficult to make the heat exchanger compact.
　本発明は上記状況に鑑みてなされたもので、その目的は、高い熱交換率を有し、製造が容易で、コンパクトに構成できる熱交換器用伝熱管とそれを用いた熱交換器を提供することにある。 The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger tube for a heat exchanger that has a high heat exchange rate, is easy to manufacture, and can be configured compactly, and a heat exchanger using the heat exchanger tube. There is.
　次に、上記の課題を解決するための手段を、実施の形態に対応する図面を参照して説明する。
　本発明の請求項１記載の熱交換器用伝熱管１１は、外管１３と、
　前記外管１３の中に挿通され軸線直交断面において相互の軸線間距離が実質的に等しく配置される複数の内管１５と、
　外管内周面２１に少なくとも一部分が固定され前記複数の内管１５が内側に挿通される第１コイル１７と、
　それぞれの内管内周面２３に少なくとも一部分が固定される第２コイル１９と、
　前記外管１３の内側と前記内管１５の外側とで構成される第１流路２５の流路断面積Ｓ１と、
　それぞれの前記内管１５の流路断面積を合計して構成され前記流路断面積Ｓ１との比がＳ１：Ｓ２＝１：２～２：１の範囲である第２流路２７の流路断面積Ｓ２と、
　を具備することを特徴とする。 Next, means for solving the above problems will be described with reference to the drawings corresponding to the embodiments.
The heat exchanger heat exchanger tube 11 according to claim 1 of the present invention includes an outer tube 13,
A plurality of inner pipes 15 that are inserted into the outer pipe 13 and arranged so that the distances between the axes in the cross section perpendicular to the axis are substantially equal;
A first coil 17 that is at least partially fixed to the inner peripheral surface 21 of the outer tube and through which the plurality of inner tubes 15 are inserted;
A second coil 19 at least partially fixed to the inner peripheral surface 23 of each inner tube;
A channel cross-sectional area S1 of the first channel 25 configured by the inside of the outer tube 13 and the outside of the inner tube 15;
The flow path of the second flow path 27 which is configured by summing the flow path cross-sectional areas of the respective inner pipes 15 and whose ratio to the flow path cross-sectional area S1 is in the range of S1: S2 = 1: 2 to 2: 1. Cross-sectional area S2,
It is characterized by comprising.
　この熱交換器用伝熱管１１では、外管１３が、外管内周面２１に一部分を固定する第１コイル１７を有し、それぞれの内管１５が、内管内周面２３に一部分を固定する第２コイル１９を有する。第１コイル１７及び第２コイル１９は、流体を乱す役割、及び伝熱を促進する役割を果たす。
　第１コイル１７の内側には、複数の内管１５が挿通される。これにより、内管１５は、１本である場合に比べ、第１流路２５を流れる流体との熱交換面積の調整、第２流路２７における流路断面積の調整が容易となり、且つ容易な製造方法で得られる。
　より具体的に、この調整は、内管１５の本数、内管１５の直径サイズを変えることによって行うことができる。
　外管１３の内側と内管１５の外側とで形成される第１流路２５の流路断面積Ｓ１と、内管１５の第２流路２７の流路断面積Ｓ２とは、１：２～２：１となるように構成されている。これにより、Ｓ１／Ｓ２が１／２以下となることによる第１流路２５の流路断面積の不足が生じなくなる。また、Ｓ１／Ｓ２が２／１以上となる第２流路２７の流路断面積の不足が生じなくなる。このように、内管１５を複数にすることで、第１流路２５と第２流路２７との流路断面積比が調整しやすくなり、流路断面積比を好ましい比に近づけることが容易に可能となる。 In this heat exchanger heat transfer tube 11, the outer tube 13 has a first coil 17 that is partially fixed to the inner peripheral surface 21 of the outer tube, and each of the inner tubes 15 is fixed to the inner peripheral surface 23 of the inner tube. Two coils 19 are provided. The 1st coil 17 and the 2nd coil 19 play a role which disturbs fluid, and promotes heat transfer.
A plurality of inner pipes 15 are inserted inside the first coil 17. Thereby, compared with the case where the number of the inner pipes 15 is one, the adjustment of the heat exchange area with the fluid flowing through the first flow path 25 and the adjustment of the cross-sectional area of the flow path in the second flow path 27 are easier and easier. Obtained by a simple manufacturing method.
More specifically, this adjustment can be performed by changing the number of inner tubes 15 and the diameter size of the inner tubes 15.
The flow path cross-sectional area S1 of the first flow path 25 formed by the inner side of the outer pipe 13 and the outer side of the inner pipe 15 and the flow path cross-sectional area S2 of the second flow path 27 of the inner pipe 15 are 1: 2. It is configured to be ˜2: 1. Thereby, the shortage of the channel cross-sectional area of the first channel 25 due to S1 / S2 being 1/2 or less does not occur. In addition, there is no shortage of the channel cross-sectional area of the second channel 27 where S1 / S2 is 2/1 or more. As described above, by using a plurality of inner pipes 15, it is easy to adjust the flow path cross-sectional area ratio between the first flow path 25 and the second flow path 27, and the flow path cross-sectional area ratio can be brought close to a preferable ratio. Easy to do.
　本発明の請求項２記載の熱交換器用伝熱管１１は、請求項１記載の熱交換器用伝熱管１１であって、
　前記第１流路２５の任意の位置に、前記内管１５に沿って芯材が挿通されていることを特徴とする。 The heat exchanger tube 11 for a heat exchanger according to claim 2 of the present invention is the heat exchanger tube 11 for a heat exchanger according to claim 1,
A core material is inserted along the inner pipe 15 at an arbitrary position of the first flow path 25.
　この熱交換器用伝熱管１１では、第１流路２５に芯材が設けられることで、第１流路２５を流れる流体が分散されやすくなる。すなわち、第１流路２５の流路断面積における半径方向内側と半径方向外側とを流れる流体の移動が促進され、温度勾配が得やすくなる。その結果、熱交換率が高まる。また、芯材が配置される部分の第１流路２５を流れる流体が排除できるので、第１流路２５の流路断面積を削減調整することができる。 In the heat exchanger tube 11 for heat exchanger, since the core material is provided in the first flow path 25, the fluid flowing through the first flow path 25 is easily dispersed. That is, the movement of the fluid flowing in the radial inner side and the radial outer side in the channel cross-sectional area of the first channel 25 is promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased. In addition, since the fluid flowing through the first flow path 25 at the portion where the core material is disposed can be eliminated, the flow path cross-sectional area of the first flow path 25 can be reduced and adjusted.
　本発明の請求項３記載の熱交換器用伝熱管１１は、請求項２記載の熱交換器用伝熱管１１であって、
　前記芯材が、中実棒２９であることを特徴とする。 The heat exchanger tube 11 for a heat exchanger according to claim 3 of the present invention is the heat exchanger tube 11 for a heat exchanger according to claim 2,
The core material is a solid bar 29.
　この熱交換器用伝熱管１１では、第１流路２５を流れる流体が、中実棒２９の体積分で効果的に排除可能となる。 In the heat exchanger tube 11 for heat exchanger, the fluid flowing through the first flow path 25 can be effectively removed by the volume of the solid rod 29.
　本発明の請求項４記載の熱交換器用伝熱管１１は、請求項２記載の熱交換器用伝熱管１１であって、
　前記芯材が、コイル部材であることを特徴とする。 The heat exchanger tube 11 for heat exchanger according to claim 4 of the present invention is the heat exchanger tube 11 for heat exchanger according to claim 2,
The core material is a coil member.
　この熱交換器用伝熱管１１では、第１流路２５のコイル部材近傍を流れる流体の流れを乱す、或いは撹拌することが可能となる。この撹拌によって、第１流路２５の流路断面積における半径方向内側と半径方向外側とを流れる流体の移動がより効果的に促進され、温度勾配が得やすくなる。その結果、熱交換率が高まる。 In the heat exchanger tube 11 for heat exchanger, it is possible to disturb or stir the flow of the fluid flowing in the vicinity of the coil member of the first flow path 25. By this stirring, the movement of the fluid flowing through the radially inner side and the radially outer side in the channel cross-sectional area of the first channel 25 is more effectively promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased.
　本発明の請求項５記載の熱交換器用伝熱管は、請求項２記載の熱交換器用伝熱管であって、
　前記芯材が、螺旋状に形成される帯板状部材４７であることを特徴とする。 The heat exchanger tube for a heat exchanger according to claim 5 of the present invention is the heat exchanger tube for a heat exchanger according to claim 2,
The core material is a strip-like member 47 formed in a spiral shape.
　この熱交換器用伝熱管４５では、第１流路２５を流れる流体の流れを帯板状部材４７が螺旋状に形成されることによって乱す、或いは撹拌することが可能となる。この撹拌によって、第１流路２５の流路断面積における半径方向内側と半径方向外側とを流れる流体の移動がより効果的に促進され、温度勾配が得やすくなる。その結果、熱交換率が高まる。 In the heat exchanger heat transfer tube 45, the flow of the fluid flowing through the first flow path 25 can be disturbed or agitated by forming the strip plate member 47 in a spiral shape. By this stirring, the movement of the fluid flowing through the radially inner side and the radially outer side in the channel cross-sectional area of the first channel 25 is more effectively promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased.
　本発明の請求項６記載の熱交換器用伝熱管１１は、請求項１，２，３，４，５のいずれか１つに記載の熱交換器用伝熱管であって、
　屈曲部を備えることを特徴とする。 The heat exchanger tube 11 for heat exchanger according to claim 6 of the present invention is the heat exchanger tube for heat exchanger according to any one of claims 1, 2, 3, 4, and 5,
A bent portion is provided.
　この熱交換器用伝熱管１１では、管形状として、その中途部分などを任意の角度で曲げ屈曲部を有した構成にすることができ、また、この屈曲部の位置において、屈曲形成する場合に、外管と内管とには第１コイル及び第２コイルとを有することで潰れてしまうことがない。そして、この屈曲部を備える形状とすることで、両端の流路出入口を任意の向きに構成でき、伝熱管としての長さを有しながら全体的な大きさをコンパクトに形成できる。 In the heat exchanger tube 11 for heat exchanger, as a tube shape, it is possible to have a configuration in which a middle portion or the like has a bent portion at an arbitrary angle, and when the bent portion is formed at the position of the bent portion, The outer tube and the inner tube are not crushed by having the first coil and the second coil. And by setting it as the shape provided with this bending part, the flow path inlet / outlet of both ends can be comprised in arbitrary directions, and the whole magnitude | size can be compactly formed, having the length as a heat exchanger tube.
　本発明の請求項７記載の熱交換器用伝熱管１１は、請求項１，２，３，４，５のいずれか１つに記載の熱交換器用伝熱管１１であって、
　同一平面上において同一の半径及び同一の曲げ角度で逆方向に曲げられる一対の第１屈曲部３１及び第２屈曲部３３を備えることを特徴とする。 The heat exchanger tube 11 for a heat exchanger according to claim 7 of the present invention is the heat exchanger tube 11 for a heat exchanger according to any one of claims 1, 2, 3, 4, and 5,
It is characterized by comprising a pair of first bent portion 31 and second bent portion 33 which are bent in the opposite direction with the same radius and the same bending angle on the same plane.
　この熱交換器用伝熱管１１では、管形状を、同一の半径及び同一の曲げ角度で逆向きに曲げるＳ字形状とすることで、各管の屈曲部の長さ変動を相殺できる。これにより、屈曲形成以前の真直状態の長さを全て揃えることができて、Ｓ字形状に屈曲形成後、各管の端部を面一に揃えることが可能となる。 In this heat exchanger tube 11 for heat exchangers, the length variation of the bent portion of each tube can be offset by making the tube shape into an S shape that is bent in the opposite direction with the same radius and the same bending angle. This makes it possible to align all the straight lengths before the formation of the bend, and after forming the bend into an S-shape, it is possible to align the ends of the tubes.
　本発明の請求項８記載の熱交換器は、請求項１～７のいずれか１つに記載の熱交換器用伝熱管を備えることを特徴とする。 A heat exchanger according to an eighth aspect of the present invention includes the heat exchanger tube for a heat exchanger according to any one of the first to seventh aspects.
　この熱交換器では、１本の外管の内側に複数本の内管を挿通して構成されるとともに、各流路にコイルを配設した構成とされる熱交換器用伝熱管よりなるので、熱交換率が向上した熱交換器となり、また、このことからコンパクトに構成することができる。 Since this heat exchanger consists of a plurality of inner tubes inserted inside one outer tube and a heat exchanger tube for a heat exchanger having a coil disposed in each flow path, The heat exchanger has an improved heat exchange rate, and can be configured compactly.
　本発明に係る請求項１記載の熱交換器用伝熱管によれば、内管を複数で構成するとともに、各流路にコイルを配設したので、高い熱交換率を有し、製造が容易で、コンパクトに構成できる。 According to the heat exchanger tube for a heat exchanger according to claim 1 of the present invention, since the inner tube is composed of a plurality of coils and the coil is disposed in each flow path, it has a high heat exchange rate and is easy to manufacture. Can be configured compactly.
　本発明に係る請求項２記載の熱交換器用伝熱管によれば、第１流路を流れる流体への熱伝達率を高めることができ、且つ第１流路と第２流路との流路断面積比を調整容易とすることができる。 According to the heat exchanger heat transfer tube of the second aspect of the present invention, the heat transfer rate to the fluid flowing through the first flow path can be increased, and the flow path between the first flow path and the second flow path. The cross-sectional area ratio can be easily adjusted.
　本発明に係る請求項３記載の熱交換器用伝熱管によれば、第１流路内に配置される中実棒よりなる芯材によって、第１流路の流路断面積を効果的に減少させ、すなわち削減調整することができる。 According to the heat exchanger tube for a heat exchanger according to claim 3 of the present invention, the flow path cross-sectional area of the first flow path is effectively reduced by the core made of the solid rod arranged in the first flow path. That is, reduction adjustment can be performed.
　本発明に係る請求項４記載の熱交換器用伝熱管によれば、第１流路内に配置されるコイル部材によって、第１流路の流路断面積を減少させながら、第１流路を流れる流体を撹拌して熱交換率を向上させることができる。 According to the heat exchanger tube for heat exchanger according to claim 4 of the present invention, the first flow path is reduced while the flow path cross-sectional area of the first flow path is reduced by the coil member disposed in the first flow path. The flowing fluid can be agitated to improve the heat exchange rate.
　本発明に係る請求項５記載の熱交換器用伝熱管によれば、第１流路内に配置される螺旋形状の帯板状部材によって、第１流路の流路断面積を減少させながら、第１流路を流れる流体を撹拌して熱交換率を向上させることができる。 According to the heat exchanger tube for heat exchanger according to claim 5 of the present invention, while reducing the flow passage cross-sectional area of the first flow path by the spiral strip-shaped member disposed in the first flow path, The fluid flowing through the first flow path can be agitated to improve the heat exchange rate.
　本発明に係る請求項６記載の熱交換器用伝熱管によれば、屈曲部を備えることにより、伝熱管として任意の形状に構成でき、コンパクト化を可能とする。 According to the heat exchanger tube for a heat exchanger according to claim 6 of the present invention, by providing the bent portion, the heat exchanger tube can be configured in an arbitrary shape and can be made compact.
　本発明に係る請求項７記載の熱交換器用伝熱管によれば、屈曲部を同一の半径及び同一の曲げ角度で互いに逆方向としてＳ字形状に形成したので、内外各管の端部を面一として、コンパクト化可能な屈曲構造の製造を、容易にすることができる。 According to the heat exchanger tube for a heat exchanger according to claim 7 of the present invention, since the bent portions are formed in an S shape with the same radius and the same bending angle as opposite directions, the end portions of the inner and outer tubes are faced. For one thing, it is possible to easily manufacture a bendable structure that can be made compact.
　本発明に係る請求項８記載の熱交換器によれば、１本の外管の内側に複数本の内管を挿通して構成されるとともに、各流路にコイルを配設した構成とされる熱交換器用伝熱管よりなるので、熱交換率が向上した熱交換器を得ることができる。また、このことから伝熱管の長さを短く構成でき、かつ伝熱管を屈曲させることも可能であることから、熱交換器としてコンパクトに構成することができる。 According to the heat exchanger according to claim 8 of the present invention, a plurality of inner pipes are inserted inside one outer pipe, and a coil is provided in each flow path. Therefore, a heat exchanger having an improved heat exchange rate can be obtained. Moreover, since the length of a heat exchanger tube can be comprised from this and a heat exchanger tube can also be bent, it can be comprised compactly as a heat exchanger.
本発明の実施形態に係る熱交換器用伝熱管の一部分を切り欠いた要部側面図である。It is a principal part side view which notched a part of heat exchanger tube for heat exchangers which concerns on embodiment of this invention. 図１に示した熱交換器用伝熱管の軸線直交方向の断面図である。It is sectional drawing of the axis line orthogonal direction of the heat exchanger tube for heat exchangers shown in FIG. Ｓ字形状に形成された熱交換器用伝熱管の平面図である。It is a top view of the heat exchanger tube for heat exchangers formed in S shape. 図３のＡ－Ａ矢視図である。FIG. 4 is a view taken along arrow AA in FIG. 3. 図３のＢ－Ｂ断面図である。FIG. 4 is a sectional view taken along line BB in FIG. 3. 図３のＣ－Ｃ断面図である。FIG. 4 is a sectional view taken along the line CC of FIG. 3. 芯材が省略された変形例に係る熱交換器用伝熱管の断面図である。It is sectional drawing of the heat exchanger tube for heat exchangers which concerns on the modification in which the core material was abbreviate | omitted. 図７に示した熱交換器用伝熱管の軸線直交方向の断面図である。It is sectional drawing of the axis orthogonal direction of the heat exchanger tube for heat exchangers shown in FIG. 芯材の変形例に係る熱交換器用伝熱管の断面図である。It is sectional drawing of the heat exchanger tube for heat exchangers which concerns on the modification of a core material. 図９に示した熱交換器用伝熱管の軸線直交方向の断面図である。FIG. 10 is a cross-sectional view in the direction perpendicular to the axis of the heat exchanger tube for heat exchanger shown in FIG. 9.
　以下、本発明に係る実施形態を図面を参照して説明する。
　図１は本発明の実施形態に係る熱交換器用伝熱管の一部分を切り欠いた要部側面図、図２は図１に示した熱交換器用伝熱管の軸線直交方向の断面図、図３はＳ字形状に形成された熱交換器用伝熱管の平面図、図４は図３のＡ－Ａ矢視図、図５は図３のＢ－Ｂ断面図、図６は図３のＣ－Ｃ断面図である。
　本実施形態に係る熱交換器用伝熱管１１は、外管１３と、内管１５と、第１コイル１７と、第２コイル１９と、流路断面積Ｓ１と、流路断面積Ｓ２と、を構成に有する。
　外管１３は、軸線直交断面の形状が円形状に形成される。外管１３及び内管１５の材質には、例えば銅やステンレス鋼等を用いることができる。この他、同等程度の熱伝導率を有し、耐熱温度、耐腐食性、強度が確保されればその他の金属や合金であってもよい。なお、外管１３及び内管１５は、継目無しのシームレス管または電縫管の何れであってもよい。 Embodiments according to the present invention will be described below with reference to the drawings.
FIG. 1 is a side view of a principal part of a heat exchanger tube for heat exchanger according to an embodiment of the present invention, a part of which is cut away, FIG. 2 is a cross-sectional view of the heat exchanger tube for heat exchanger shown in FIG. 4 is a plan view of the heat exchanger tube for heat exchanger formed in an S-shape, FIG. 4 is a view taken along the line AA in FIG. 3, FIG. 5 is a cross-sectional view along BB in FIG. 3, and FIG. It is sectional drawing.
The heat exchanger tube 11 for a heat exchanger according to the present embodiment includes an outer tube 13, an inner tube 15, a first coil 17, a second coil 19, a channel cross-sectional area S1, and a channel cross-sectional area S2. Have in the configuration.
The outer tube 13 is formed in a circular shape in the cross section orthogonal to the axis. For example, copper or stainless steel can be used as the material of the outer tube 13 and the inner tube 15. In addition, other metals and alloys may be used as long as they have the same degree of thermal conductivity and heat resistance temperature, corrosion resistance, and strength are ensured. The outer tube 13 and the inner tube 15 may be seamless seamless tubes or electric sewing tubes.
　内管１５は、複数、本実施形態では４本のものからなり、外管１３の中に軸線同士が同方向に平行となって挿通され、軸線直交断面において相互の軸線間距離が実質的に等しく配置される。すなわち、４本の内管１５は、外管１３の軸線からそれぞれの軸線までの距離が実質的に等しくなるように配置される。また、熱交換が均等に行われるように、４本の内管１５は、それぞれの軸線を結んだ線が、断面視で正多角形状、例えば正方形状になるように配置されることが好ましい。さらに、４本の内管１５は、各管の外周面同士が離間していることが好ましい。これにより、外管１３の内側で流体を均等に流すことができる。なお、上記した「相互の軸線間距離が実質的に等しい」とは、最も長い軸線間距離が、最も短い軸線間距離の１００～１２０％の範囲内であることをいう。 The inner tube 15 includes a plurality of inner tubes 15 in the present embodiment. The inner tubes 15 are inserted into the outer tube 13 in parallel with each other in the same direction. Equally arranged. That is, the four inner pipes 15 are arranged so that the distances from the axis of the outer pipe 13 to the respective axes are substantially equal. Moreover, it is preferable that the four inner pipes 15 are arranged so that the lines connecting the respective axes are in a regular polygonal shape, for example, a square shape in a cross-sectional view, so that heat exchange is performed evenly. Furthermore, it is preferable that the outer peripheral surfaces of the four inner pipes 15 are separated from each other. Thereby, the fluid can be made to flow evenly inside the outer tube 13. Note that “the mutual distance between the axes is substantially equal” means that the longest distance between the axes is within a range of 100 to 120% of the shortest distance between the axes.
　なお、内管１５の数は、４本に限定されず、２本、３本、または５本以上であってもよい。 The number of inner tubes 15 is not limited to four, and may be two, three, or five or more.
　第１コイル１７は、外管内周面２１に少なくとも一部分が固定される。この第１コイル１７の内側に、複数の内管１５が挿通される。なお、４本の内管１５は、第１コイル１７に接するように配置されていてもよい。 The first coil 17 is at least partially fixed to the inner peripheral surface 21 of the outer tube. A plurality of inner pipes 15 are inserted inside the first coil 17. The four inner pipes 15 may be arranged so as to be in contact with the first coil 17.
　第２コイル１９は、それぞれの内管内周面２３に少なくとも一部分が固定される。本実施形態において、それぞれの第２コイル１９は、同一形状で形成される。
　第１コイル１７及び第２コイル１９は、上記同様の導電性良好な金属の線材からなり、螺旋状に巻かれることでコイルスプリング状となる。第１コイル１７及び第２コイル１９は、例えばロウ付けによって外管内周面２１、内管内周面２３に固定される。 The second coil 19 is at least partially fixed to the inner peripheral surface 23 of each inner tube. In the present embodiment, each second coil 19 is formed in the same shape.
The 1st coil 17 and the 2nd coil 19 consist of a metal wire with the same favorable electroconductivity as the above, and become coil spring shape by being wound spirally. The first coil 17 and the second coil 19 are fixed to the inner peripheral surface 21 of the outer tube and the inner peripheral surface 23 of the inner tube by brazing, for example.
　ここで、外管１３の内側と内管１５の外側とで構成される第１流路２５は、流路断面積Ｓ１とする。また、それぞれの内管１５の流路断面積を合計して構成される第２流路２７は、流路断面積Ｓ２とする。熱交換器用伝熱管１１は、流路断面積Ｓ１と流路断面積Ｓ２との比が、Ｓ１：Ｓ２＝１：２～２：１の範囲で設定されている。なお、この流路断面積Ｓ１と流路断面積Ｓ２との比は、Ｓ１：Ｓ２＝５：９～９：５が好ましく、Ｓ１：Ｓ２＝４：５～５：４がより好ましい。 Here, the first flow path 25 constituted by the inner side of the outer pipe 13 and the outer side of the inner pipe 15 is assumed to be a flow path cross-sectional area S1. In addition, the second flow path 27 configured by summing the flow path cross-sectional areas of the respective inner pipes 15 is defined as a flow path cross-sectional area S2. In the heat exchanger tube 11 for heat exchanger, the ratio of the channel cross-sectional area S1 and the channel cross-sectional area S2 is set in the range of S1: S2 = 1: 2 to 2: 1. The ratio of the channel cross-sectional area S1 to the channel cross-sectional area S2 is preferably S1: S2 = 5: 9 to 9: 5, and more preferably S1: S2 = 4: 5 to 5: 4.
　第１流路２５の任意の位置には、内管１５に沿って芯材が挿通されている。芯材を設けることにより、第１流路２５を流れる流体を分散させることができる。また、芯材は、流路断面積Ｓ１と流路断面積Ｓ２の流路断面積比を調整するための手段とすることができる。外管１３の中心には、中実棒２９を同軸で配設してもよい。その場合、第１流路２５を流れる流体が外管１３内で均等に流れるように、中実棒２９と内管１５の外周面とは離間していることが好ましい。 A core material is inserted along the inner pipe 15 at an arbitrary position of the first flow path 25. By providing the core material, the fluid flowing through the first flow path 25 can be dispersed. Further, the core material can be used as a means for adjusting the channel cross-sectional area ratio between the channel cross-sectional area S1 and the channel cross-sectional area S2. A solid bar 29 may be coaxially disposed at the center of the outer tube 13. In that case, it is preferable that the solid rod 29 and the outer peripheral surface of the inner tube 15 are separated from each other so that the fluid flowing through the first flow path 25 flows evenly in the outer tube 13.
　また、上記の流体分散効果、流路断面積比調整効果が得られるものであれば、芯材は、中実棒２９に限らず、コイル部材や、帯板状部材４７等であってもよい。また、芯材の位置は、流体分散効果、流路断面積比調整効果が得られるものであれば、軸線が外管１３の軸線とずれていてもよい。また、芯材は、上記効果が得られるものであれば、外管１３と隣り合う２本の内管１５とで形成される略三角形部分に配置されてもよく、各内管１５のそれぞれと外管１３とで形成される計４つの略三角形部分に１つずつ合計４つのものが配置されてもよい。 In addition, the core material is not limited to the solid rod 29, and may be a coil member, a strip plate member 47, or the like as long as the fluid dispersion effect and the flow path cross-sectional area ratio adjustment effect can be obtained. . The position of the core material may be shifted from the axis of the outer tube 13 as long as the fluid dispersion effect and the flow path cross-sectional area ratio adjustment effect can be obtained. In addition, the core material may be disposed in a substantially triangular portion formed by the outer tube 13 and the two inner tubes 15 adjacent to each other as long as the above-described effect can be obtained. A total of four things may be arrange | positioned one each in a total of four substantially triangular parts formed with the outer tube | pipe 13. FIG.
　より具体的に、外管１３は、外径を１０ｍｍ、内径を８．４ｍｍ、厚さを０．８ｍｍとし、内管１５は、外径を３ｍｍ、内径を２．５ｍｍ、厚さを０．２５ｍｍとして、第１コイル１７は、線径を０．３ｍｍ、内径を７．５ｍｍ、外径を８．１ｍｍとするとともに、第２コイル１９は、線径を０．３ｍｍ、内径を１．７ｍｍ、外径を２．３ｍｍとして、さらに、芯材は、直径を１ｍｍとすると、これら数値により、例えば流路断面積Ｓ１は、１５．１ｍｍ2 、流路断面積Ｓ２は、９．０８ｍｍ2 と算出される。この場合、流路断面積Ｓ１と流路断面積Ｓ２との流路断面積比は、Ｓ１：Ｓ２＝１：１．６６となる。 More specifically, the outer tube 13 has an outer diameter of 10 mm, an inner diameter of 8.4 mm, and a thickness of 0.8 mm. The inner tube 15 has an outer diameter of 3 mm, an inner diameter of 2.5 mm, and a thickness of 0.2 mm. The first coil 17 has a wire diameter of 0.3 mm, an inner diameter of 7.5 mm, an outer diameter of 8.1 mm, and the second coil 19 has a wire diameter of 0.3 mm and an inner diameter of 1.7 mm. the outer diameter as 2.3 mm, furthermore, the core, when the 1mm diameter, these numerical values, for example, flow path cross-sectional area S1 is 15.1 mm 2, flow path cross-sectional area S2 is a by 9.08 2 Calculated. In this case, the channel cross-sectional area ratio between the channel cross-sectional area S1 and the channel cross-sectional area S2 is S1: S2 = 1: 1.66.
　熱交換器用伝熱管１１は、図３に示すように、同一平面上において、同一の半径及び同一の曲げ角度Ｒ、例えば１８０°で逆方向に曲げられる一対の第１屈曲部３１及び第２屈曲部３３によってＳ字形状に形成することができる。 As shown in FIG. 3, the heat exchanger heat transfer tube 11 has a pair of first bent portion 31 and second bent portion that are bent in the same direction and at the same radius and the same bending angle R, for example, 180 °. The portion 33 can be formed into an S shape.
　この場合、外管１３の両端にはＴ型ジョイント３５の一端が接続される。それぞれのＴ型ジョイント３５は、外管１３と反対側の端に、ソケット３７が接続される。ソケット３７は、Ｔ型ジョイント３５の内側に開放された第１流路２５を閉塞して、内管１５を外部へ導出する。外部へ導出されたそれぞれの内管１５は、別のソケット３９に外周が水密にシールされて挿通される。それぞれの内管１５の第２流路２７は、このソケット３９の内側で開放される。また、第１流路２５が開放されたＴ型ジョイント３５の残りの接続部には、接続パイプ４１が接続される。第１流路２５は、Ｔ型ジョイント３５を介してこの接続パイプ４１に接続される。 In this case, one end of a T-shaped joint 35 is connected to both ends of the outer tube 13. Each T-shaped joint 35 is connected to a socket 37 at the end opposite to the outer tube 13. The socket 37 closes the first flow path 25 opened to the inside of the T-shaped joint 35 and leads the inner tube 15 to the outside. Each inner pipe 15 led out to the outside is inserted into another socket 39 with its outer periphery sealed in a watertight manner. The second flow path 27 of each inner tube 15 is opened inside the socket 39. The connection pipe 41 is connected to the remaining connection portion of the T-shaped joint 35 in which the first flow path 25 is opened. The first flow path 25 is connected to the connection pipe 41 via the T-shaped joint 35.
　図７は芯材が省略された変形例に係る熱交換器用伝熱管４３の断面図、図８は図７に示した熱交換器用伝熱管４３の軸線直交方向の断面図、図９は芯材の変形例に係る熱交換器用伝熱管４５の断面図、図１０は図９に示した熱交換器用伝熱管４５の軸線直交方向の断面図である。
　なお、上記の熱交換器用伝熱管１１は、図７，図８に示すように、芯材を省略するものであってもよい。また、芯材がコイル部材の場合、流路断面積比に応じて、例えば、巻き数や線径等を変えてもよい。さらに、図９，図１０に示すように、芯材の形状を、上述した中実棒２９ではなく、螺旋状に形成される帯板状部材４７として構成することとしてもよい。また、内管１５のそれぞれに挿入される第２コイル１９は、挿入される内管１５ごとに形状、巻き数、線径等の異なるものを用いてもよい。 7 is a cross-sectional view of a heat exchanger tube 43 for a heat exchanger according to a modification in which the core material is omitted, FIG. 8 is a cross-sectional view of the heat exchanger tube 43 for heat exchanger shown in FIG. 7, and FIG. 9 is a core material. FIG. 10 is a cross-sectional view of the heat exchanger tube 45 for heat exchanger shown in FIG. 9 in a direction orthogonal to the axis line.
In addition, as shown to FIG. 7, FIG. 8, the said heat exchanger tube 11 for heat exchangers may abbreviate | omit a core material. Further, when the core material is a coil member, the number of turns, the wire diameter, and the like may be changed according to the flow path cross-sectional area ratio. Furthermore, as shown in FIGS. 9 and 10, the shape of the core material may be configured as a strip-like member 47 formed in a spiral shape instead of the solid rod 29 described above. Further, the second coil 19 inserted into each of the inner tubes 15 may be different in shape, number of turns, wire diameter, etc. for each inserted inner tube 15.
　次に、上記構成を有する熱交換器用伝熱管１１の作用を説明する。
　熱交換器用伝熱管１１では、外管１３が、外管内周面２１に一部分を固定する第１コイル１７を有し、それぞれの内管１５が、内管内周面２３に一部分を固定する第２コイル１９を有する。第１コイル１７及び第２コイル１９は、それぞれの管内を流れる流体を乱す役割、及び伝熱を促進する役割を果たす。 Next, the effect | action of the heat exchanger tube 11 for heat exchangers which has the said structure is demonstrated.
In the heat exchanger tube 11 for heat exchanger, the outer tube 13 has a first coil 17 that fixes a part to the inner peripheral surface 21 of the outer tube, and each inner tube 15 fixes a second part to the inner peripheral surface 23 of the inner tube. It has a coil 19. The 1st coil 17 and the 2nd coil 19 play the role which disturbs the fluid which flows through each pipe, and the role which promotes heat transfer.
　第１コイル１７の内側には、複数の内管１５が挿通される。これにより、内管１５は、１本である場合に比べ、第１流路２５を流れる流体との熱交換面積の調整、第２流路２７における流路断面積の調整が容易となり、また、容易な製造方法で得られる。
　より具体的に、この調整は、内管１５の本数、内管１５の直径サイズ、内管１５の厚さを変えることによって行うことができる。 A plurality of inner pipes 15 are inserted inside the first coil 17. This makes it easier to adjust the heat exchange area with the fluid flowing through the first flow path 25 and to adjust the cross-sectional area of the flow path in the second flow path 27 than when there is only one inner tube 15. It is obtained by an easy manufacturing method.
More specifically, this adjustment can be performed by changing the number of the inner tubes 15, the diameter size of the inner tubes 15, and the thickness of the inner tubes 15.
　外管１３の内側と内管１５の外側とで形成される第１流路２５の流路断面積Ｓ１と、内管１５の第２流路２７の流路断面積Ｓ２とは、１：２～２：１となるように構成されている。これにより、Ｓ１／Ｓ２が１／２以下となることによる第１流路２５の流路断面積の不足が生じなくなる。また、Ｓ１／Ｓ２が２／１以上となる第２流路２７の流路断面積の不足が生じなくなる。このように、内管１５を複数にすることで、第１流路２５と第２流路２７との流路断面積比が調整しやすくなり、流路断面積比をより好ましい比に近づけることが容易に可能となる。 The flow path cross-sectional area S1 of the first flow path 25 formed by the inner side of the outer pipe 13 and the outer side of the inner pipe 15 and the flow path cross-sectional area S2 of the second flow path 27 of the inner pipe 15 are 1: 2. It is configured to be ˜2: 1. Thereby, the shortage of the channel cross-sectional area of the first channel 25 due to S1 / S2 being 1/2 or less does not occur. Further, the shortage of the channel cross-sectional area of the second channel 27 in which S1 / S2 is 2/1 or more does not occur. As described above, by using a plurality of inner pipes 15, the flow passage cross-sectional area ratio between the first flow passage 25 and the second flow passage 27 can be easily adjusted, and the flow passage cross-sectional area ratio is brought closer to a more preferable ratio. Is easily possible.
　また、熱交換器用伝熱管１１では、第１流路２５に芯材である中実棒２９や帯板状部材４７が設けられることで、第１流路２５を流れる流体が分散されやすくなる。すなわち、第１流路２５の流路断面積における半径方向内側と半径方向外側とを流れる流体の移動が促進され、温度勾配が得やすくなる。その結果、熱交換率が高まる。また、芯材が配置される部分の第１流路２５を流れる流体が排除できるので、第１流路２５の流路断面積を削減調整することができる。これにより、第１流路２５を流れる流体への熱伝達率を高め、且つ第１流路２５と第２流路２７との流路断面積比を調整容易とすることができる。 Moreover, in the heat exchanger tube 11 for the heat exchanger, the fluid flowing through the first flow path 25 is easily dispersed by providing the first flow path 25 with the solid rod 29 and the strip plate member 47 as the core material. That is, the movement of the fluid flowing in the radial inner side and the radial outer side in the channel cross-sectional area of the first channel 25 is promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased. In addition, since the fluid flowing through the first flow path 25 at the portion where the core material is disposed can be eliminated, the flow path cross-sectional area of the first flow path 25 can be reduced and adjusted. Thereby, the heat transfer rate to the fluid flowing through the first flow path 25 can be increased, and the flow path cross-sectional area ratio between the first flow path 25 and the second flow path 27 can be easily adjusted.
　そして、芯材を中実棒２９とすれば、第１流路２５を流れる流体が、中実棒２９の体積分で排除可能となる。その結果、第１流路２５の流路断面積を効果的に減少させ、削減調整することができる。また、この中実棒２９の体積の増減によって、内管１５の厚さの増減を可能とし、流路断面積比を調整することができる。 If the core material is the solid rod 29, the fluid flowing through the first flow path 25 can be eliminated by the volume of the solid rod 29. As a result, the channel cross-sectional area of the first channel 25 can be effectively reduced and reduced and adjusted. Further, by increasing or decreasing the volume of the solid rod 29, the thickness of the inner tube 15 can be increased or decreased, and the flow path cross-sectional area ratio can be adjusted.
　また、芯材をコイル部材や帯板状部材４７とすれば、第１流路２５のコイル部材や帯板状部材４７近傍を流れる流体の流れを乱す、或いは撹拌することが可能となる。この撹拌によって、第１流路２５の流路断面積における半径方向内側と半径方向外側とを流れる流体の移動がより効果的に促進され、温度勾配が得やすくなる。その結果、熱交換率が高まる。これにより、第１流路２５の流路断面積を減少させながら、第１流路２５を流れる流体を撹拌して熱交換率を向上させることができる。 Further, if the core member is the coil member or the strip plate member 47, the flow of the fluid flowing in the vicinity of the coil member or the strip plate member 47 of the first flow path 25 can be disturbed or agitated. By this stirring, the movement of the fluid flowing through the radially inner side and the radially outer side in the channel cross-sectional area of the first channel 25 is more effectively promoted, and a temperature gradient is easily obtained. As a result, the heat exchange rate is increased. Thereby, it is possible to improve the heat exchange rate by stirring the fluid flowing through the first flow path 25 while reducing the cross-sectional area of the first flow path 25.
　さらに、熱交換器用伝熱管１１では、管形状を、同一の半径及び同一の曲げ角度で互いに逆向きに曲げるＳ字形状とすることで、各管の屈曲部の長さ変動を相殺できる。すなわち、Ｓ字形状に屈曲形成する以前真直状態の各管の長さを全て同じで構成できて、Ｓ字形状に屈曲形成後、各管の端部を面一に揃えることが可能となる。その結果、各管の端部を面一として、コンパクト化可能な屈曲構造の製造を、容易にすることができる。 Furthermore, in the heat exchanger heat transfer tube 11, the length variation of the bent portion of each tube can be offset by making the tube shape into an S shape that is bent in the opposite directions with the same radius and the same bending angle. In other words, the length of each straight tube before being bent into the S shape can be configured to be the same, and after the bending into the S shape, the ends of the tubes can be made flush. As a result, it is possible to easily manufacture a bent structure that can be made compact with the ends of the tubes being flush.
　上述した実施形態の熱交換器用伝熱管１１，４３，４５は、複数本で構成し、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たり、複数本を束にして構成し、伝熱管列ユニットを構成し、これを熱交換器（図示せず）として構成される。
　同一平面状となるように互いが平行に配列される構成では、これをユニットとして複数段積層して熱交換器を構成することができる。積層配置された複数の伝熱管列ユニットは、例えば、各熱交換器用伝熱管のそれぞれの第１流路を接続し、また、第２流路をそれぞれに接続して、一次入口ヘッダ、一次出口ヘッダ、二次入口ヘッダ、二次出口ヘッダのそれぞれに接続される。 The heat exchanger tubes 11, 43, 45 for the heat exchanger of the above-described embodiment are configured by a plurality, and are arranged in parallel so as to be in the same plane and arranged close to each other, or a plurality of the tubes are bundled. The heat transfer tube array unit is configured, and this is configured as a heat exchanger (not shown).
In a configuration in which they are arranged in parallel so as to be in the same plane, a heat exchanger can be configured by stacking a plurality of units as a unit. The plurality of heat transfer tube array units arranged in a stack are connected to, for example, the first flow paths of the heat transfer tubes for the heat exchangers and the second flow paths are connected to the primary inlet header and the primary outlet, respectively. It is connected to each of the header, secondary inlet header, and secondary outlet header.
　そして、図示は省略するが熱交換装置側からの一次熱媒供給配管、二次熱媒供給配管、一次熱媒環流配管、及び二次熱媒環流配管の各管継手が接続されて、一次入口ヘッダに流れた一次熱媒が、例えば内管１５に流れる。内管１５を流れた一次熱媒は二次熱媒と熱交換された後、一次出口ヘッダから外部へ出る。二次入口ヘッダに流れた二次熱媒は外管１３に流れる。外管１３を流れた二次熱媒は一次熱媒と熱交換された後、二次出口ヘッダから外部へ出る。 And although illustration is omitted, 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 exchanger side are connected to the primary inlet. The primary heat medium that has flowed to the header flows to the inner tube 15, for example. The primary heating medium that has flowed through the inner pipe 15 is exchanged with the secondary heating medium, and then exits from the primary outlet header. The secondary heat medium that has flowed to the secondary inlet header flows to the outer tube 13. The secondary heat medium that has flowed through the outer tube 13 is exchanged with the primary heat medium and then exits from the secondary outlet header.
　上記構成の熱交換器によれば、内管１５の中を流れる熱媒が、内管１５の内側に設けられた第２コイル１９によって流れが乱れ、撹拌されながら流れることとなって、従来に比べて伝熱が促進され、熱交換が行われる。そして、外管１３と内管１５との間隙を流れる他系統の熱媒と熱交換される。また、この熱交換器は、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て、同一平面上に近接して並べられることで、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。 According to the heat exchanger having the above configuration, the heat medium flowing through the inner tube 15 is disturbed by the second coil 19 provided inside the inner tube 15 and flows while being stirred. In comparison, heat transfer is promoted and heat exchange is performed. Then, heat exchange is performed with a heat medium of another system that flows through the gap between the outer tube 13 and the inner tube 15. In addition, the heat exchanger includes a plurality of heat transfer tubes 11 each including an outer tube 13 and an inner tube 15 that are arranged in parallel to each other and are arranged close to each other on the same plane. Thus, it is possible to form a stacked structure, and the ground contact area can be reduced while increasing the heat transfer area.
　従って、本実施形態に係る熱交換器用伝熱管１１によれば、容易に製造でき、熱交換率が向上するので、管長を短くすることができ、また、この熱交換器用伝熱管を用いた熱交換器によれば、管長を短く構成することができてコンパクトに構成することができる。 Therefore, according to the heat exchanger tube 11 for heat exchanger according to the present embodiment, the tube length can be shortened because it can be easily manufactured and the heat exchange rate is improved, and the heat using the heat exchanger tube for heat exchanger is increased. According to the exchanger, the pipe length can be shortened and the structure can be made compact.
　１１…熱交換器用伝熱管
　１３…外管
　１５…内管
　１７…第１コイル
　１９…第２コイル
　２１…外管内周面
　２３…内管内周面
　２５…第１流路
　２７…第２流路
　２９…芯材（中実棒）
　３１…第１屈曲部
　３３…第２屈曲部
　４７…芯材（帯板状部材）
　Ｓ１、Ｓ２…流路断面積 DESCRIPTION OF SYMBOLS 11 ... Heat exchanger tube for heat exchangers 13 ... Outer tube 15 ... Inner tube 17 ... 1st coil 19 ... 2nd coil 21 ... Outer tube inner peripheral surface 23 ... Inner tube inner peripheral surface 25 ... 1st flow path 27 ... 2nd flow path 29 ... Core material (solid bar)
31 ... 1st bending part 33 ... 2nd bending part 47 ... Core material (band plate-shaped member)
S1, S2 ... cross-sectional area of flow path

Claims (8)

  1. 　外管と、
    　前記外管の中に挿通され軸線直交断面において相互の軸線間距離が実質的に等しく配置される複数の内管と、
    　外管内周面に少なくとも一部分が固定され前記複数の内管が内側に挿通される第１コイルと、
    　それぞれの内管内周面に少なくとも一部分が固定される第２コイルと、
    　前記外管の内側と前記内管の外側とで構成される第１流路の流路断面積Ｓ１と、
    　それぞれの前記内管の流路断面積を合計して構成され前記流路断面積Ｓ１との比がＳ１：Ｓ２＝１：２～２：１の範囲である第２流路の流路断面積Ｓ２と、
    を具備することを特徴とする熱交換器用伝熱管。     An outer tube,
    A plurality of inner pipes that are inserted into the outer pipe and are arranged with substantially equal distances between the axes in a cross section orthogonal to the axis;
    A first coil that is at least partially fixed to the inner peripheral surface of the outer tube, and the plurality of inner tubes are inserted inside;
    A second coil at least partially fixed to the inner peripheral surface of each inner tube;
    A cross-sectional area S1 of a first flow path constituted by the inner side of the outer pipe and the outer side of the inner pipe;
    The cross-sectional area of the second flow path is configured by summing the cross-sectional areas of the respective inner pipes, and the ratio of the cross-sectional area S1 to the flow path is S1: S2 = 1: 2 to 2: 1. S2,
    A heat exchanger tube for a heat exchanger, comprising:
  2. 　請求項１記載の熱交換器用伝熱管であって、
    　前記第１流路の任意の位置に、前記内管に沿って芯材が挿通されていることを特徴とする熱交換器用伝熱管。     A heat exchanger tube for a heat exchanger according to claim 1,
    A heat exchanger tube for a heat exchanger, wherein a core material is inserted along the inner tube at an arbitrary position of the first flow path.
  3. 　請求項２記載の熱交換器用伝熱管であって、
    　前記芯材が、中実棒であることを特徴とする熱交換器用伝熱管。     A heat exchanger tube for a heat exchanger according to claim 2,
    The heat exchanger tube for a heat exchanger, wherein the core material is a solid rod.
  4. 　請求項２記載の熱交換器用伝熱管であって、
    　前記芯材が、コイル部材であることを特徴とする熱交換器用伝熱管。     A heat exchanger tube for a heat exchanger according to claim 2,
    The heat exchanger tube for a heat exchanger, wherein the core material is a coil member.
  5. 　請求項２記載の熱交換器用伝熱管であって、
    　前記芯材が、螺旋状に形成される帯板状部材であることを特徴とする熱交換器用伝熱管。     A heat exchanger tube for a heat exchanger according to claim 2,
    The heat exchanger tube for a heat exchanger, wherein the core member is a strip-like member formed in a spiral shape.
  6. 　請求項１，２，３，４，５のいずれか１つに記載の熱交換器用伝熱管であって、
    　屈曲部を備えることを特徴とする熱交換器用伝熱管。     A heat exchanger tube for a heat exchanger according to any one of claims 1, 2, 3, 4, and 5,
    A heat exchanger tube for a heat exchanger, comprising a bent portion.
  7. 　請求項１，２，３，４，５のいずれか１つに記載の熱交換器用伝熱管であって、
    　同一平面上において同一の半径及び同一の曲げ角度で逆方向に曲げられる一対の第１屈曲部及び第２屈曲部を備えることを特徴とする熱交換器用伝熱管。     A heat exchanger tube for a heat exchanger according to any one of claims 1, 2, 3, 4, and 5,
    A heat exchanger tube for a heat exchanger, comprising a pair of first bent portions and second bent portions bent in opposite directions at the same radius and the same bending angle on the same plane.
  8. 　請求項１～７のいずれか１つに記載の熱交換器用伝熱管を備えることを特徴とする熱交換器。 A heat exchanger comprising the heat exchanger tube for a heat exchanger according to any one of claims 1 to 7.
PCT/JP2015/050327 2014-01-17 2015-01-08 Heat transfer tube for heat exchanger and heat exchanger WO2015107970A1 (en)

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WO2017116251A1 (en) 2015-12-31 2017-07-06 Aic S.A. Heat exchange device
CN111256496A (en) * 2018-11-30 2020-06-09 比亚迪股份有限公司 Heat exchanger, thermal management system of vehicle and vehicle

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JP2004218946A (en) * 2003-01-15 2004-08-05 Matsushita Electric Ind Co Ltd Heat exchanger and heat pump water heater using the same
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017116251A1 (en) 2015-12-31 2017-07-06 Aic S.A. Heat exchange device
CN111256496A (en) * 2018-11-30 2020-06-09 比亚迪股份有限公司 Heat exchanger, thermal management system of vehicle and vehicle

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