WO2014054370A1 - Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération - Google Patents

Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2014054370A1
WO2014054370A1 PCT/JP2013/073688 JP2013073688W WO2014054370A1 WO 2014054370 A1 WO2014054370 A1 WO 2014054370A1 JP 2013073688 W JP2013073688 W JP 2013073688W WO 2014054370 A1 WO2014054370 A1 WO 2014054370A1
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WO
WIPO (PCT)
Prior art keywords
tube
contact portion
heat exchanger
double
heat transfer
Prior art date
Application number
PCT/JP2013/073688
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English (en)
Japanese (ja)
Inventor
悟 梁池
加藤　央平
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to CN201380051921.4A priority Critical patent/CN104704311B/zh
Priority to EP13843545.8A priority patent/EP2916091B1/fr
Priority to US14/432,630 priority patent/US20150241132A1/en
Priority to JP2014539645A priority patent/JP5944009B2/ja
Priority to CN201320613402.XU priority patent/CN203605763U/zh
Publication of WO2014054370A1 publication Critical patent/WO2014054370A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular elements

Definitions

  • the present invention relates to a double pipe heat exchanger that forms two flow paths by combining circular pipes having different pipe diameters, and a refrigeration cycle apparatus using the double pipe heat exchanger.
  • a circular tube with a larger diameter hereinafter referred to as an outer tube
  • a circular tube with a smaller diameter hereinafter referred to as an inner tube
  • the inside of the inner pipe is used as the first flow path
  • the flow path formed between the two circular pipes is used as the second flow path
  • the heat transfer area is expanded in a bowl shape in the second flow path.
  • a method has been proposed in which a tube is inserted and brought into close contact with an inner tube and an outer tube, and the heat transfer performance is improved by the effect of expanding the heat transfer area (see, for example, Patent Document 1).
  • Patent Document 1 a double pipe heat exchanger is proposed in which a heat transfer area is expanded to increase heat transfer performance by inserting a heat transfer area expansion pipe.
  • a heat transfer area expansion tube that can efficiently improve the heat transfer performance.
  • an object of the present invention is to obtain a double-pipe heat exchanger and a refrigeration cycle apparatus that can efficiently improve heat transfer performance.
  • the double pipe heat exchanger covers the inner pipe with a larger diameter than the inner pipe through which the first fluid passes and the second fluid passes through the space between the inner pipe and the inner pipe.
  • the length of the inner contact portion that is provided in the outer tube and the space and that is in contact with the outer wall of the inner tube in the tube cross section is the tube circumference of the outer contact portion that is the contact portion with the inner wall of the outer tube.
  • the fin part between the inner contact part and the outer contact part that crosses the space in the tube cross section contacts the inner wall outer wall and the outer tube inner wall from an oblique direction so as to be longer than the length in the direction.
  • a heat transfer area expansion tube is the length of the inner contact portion that is provided in the outer tube and the space and that is in contact with the outer wall of the tube cross section.
  • the heat transfer area in contact with the outer tube and the inner tube is such that the length in the pipe circumferential direction of the contact portion with the outer wall of the inner tube is longer than the length of the contact portion with the inner wall of the outer tube. Since the expansion pipe is provided, the external force applied to the heat transfer area expansion pipe during manufacturing is dispersed, and in particular, the contact area with the inner pipe is suppressed, and the heat transfer area is expanded to improve the heat transfer performance. Can be improved.
  • FIG. 1 It is a figure explaining the structure of the double-pipe heat exchanger which concerns on Embodiment 1 of this invention. It is a figure which shows the cross section of the other direction of the double tube
  • FIG. It is a figure which shows the parameter set to the double tube type heat exchanger. It is a figure which shows the brazing part which concerns on Embodiment 4 of this invention. It is a figure which shows the refrigerating-cycle apparatus which uses the double pipe
  • FIG. 1 is a diagram illustrating the configuration of a double-pipe heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 1 shows a cross-sectional view of the double-pipe heat exchanger cut along the refrigerant flow (in particular, the inner pipe 2).
  • an inner tube 2 that is a circular tube having a smaller diameter is inserted inside an outer tube 1 that is a circular tube having a larger diameter.
  • the end of the double circular heat exchanger is in contact with the inner wall portion (outer tube inner wall) of the outer tube 1 and the outer wall portion (inner tube outer wall) of the inner tube 2 (side wall portion closing the outer tube 1). Covers the inner tube 2).
  • the inside of the inner tube 2 is defined as an inner channel 4 as a first channel, and a space formed between the inner tube 2 and the outer tube 1 is defined as an outer channel 5 as a second channel.
  • a refrigerant outlet / outlet of the outer flow path 5 is formed with a through hole in the wall surface of the outer pipe 1 to connect a connecting pipe. Then, the first fluid and the second fluid are caused to flow through the inner channel 4 and the outer channel 5, respectively. Since the first fluid and the second fluid having different temperatures flow through the respective flow paths, heat exchange between the fluids can be performed in the double-pipe heat exchanger.
  • FIG. 2 is a view showing a cross section in another direction of the double-pipe heat exchanger according to Embodiment 1 of the present invention. 2 shows a cross section taken along line A-A 'in FIG. 1 (cross-sectional view of a pipe, cut in the pipe circumferential direction when viewed from the direction in which the fluid flows).
  • the double-pipe heat exchanger of the present embodiment is configured by further inserting a heat transfer area expansion pipe 3 having a bowl-like shape having irregularities in the space portion of the outer flow path 5.
  • the inner wall (heat transfer area expansion pipe inner wall) and the inner pipe outer wall are in contact with each other at the concave part, and the outer wall (heat transfer area expansion pipe outer wall) and the outer pipe inner wall are in contact with each other at the convex part.
  • the side wall obliquely crosses the outer flow path 5 (the space between the inner tube 2 and the outer tube 1) in the tube cross section, and is in contact with the inner tube outer wall and the outer tube inner wall from an oblique direction.
  • Equation (2) the heat transfer coefficient K is expressed by equation (2).
  • ⁇ 1 is the heat transfer coefficient of the first fluid
  • d1 is the hydraulic diameter of the inner flow path 4
  • ⁇ 2 is the heat transfer coefficient of the second fluid
  • d2 is the hydraulic diameter of the outer flow path 5.
  • ⁇ is the thermal conductivity of the inner tube 2
  • dio is the outer diameter of the inner tube 2
  • dii is the inner diameter of the inner tube 2
  • R is the thermal resistance.
  • the heat transfer area expansion tube 3 acts as a fin by coming into contact with the inner tube 2, can increase the heat transfer area related to heat exchange, and increase the amount of heat exchanged between the first fluid and the second fluid. Can do.
  • the contact portion between the outer wall of the inner tube and the inner wall of the heat transfer area expanding tube is defined as an inner contact portion 6 (the length of the contacting portion in the tube circumferential direction is L1). Further, a contact portion between the inner wall of the outer tube and the outer wall of the heat transfer area expanding tube is defined as an outer contact portion 7 (the length of the contacting portion in the tube circumferential direction is L2). Further, a portion acting as a fin between the inner contact portion 6 and the outer contact portion 7 (side wall surface in the uneven shape) is referred to as a fin portion 16.
  • the double pipe type so that the inner contact portion 6 and the outer contact portion 7 are in contact with each other at one point (point contact) in the tube cross section.
  • a heat exchanger may be formed.
  • the contact portion for example, the number of fin portions 16 in the tube circumference, the heat transfer area in one fin portion 16, and the like increase, and the heat transfer area of the entire double-tube heat exchanger increases.
  • it is not a mathematical point which does not have an area etc., but has the area of the grade which ensures the reliable contact of tubes.
  • a contact part will be linear.
  • the inner contact portion 6 is formed to be point contact, the contact thermal resistance in the inner contact portion 6 increases. For this reason, the heat transfer coefficient K in Formula (2) mentioned above falls, As a result, the exchange heat quantity Q falls. Moreover, when it forms so that it may become a point contact, the location which becomes a contact failure may generate
  • the inner contact portion 6 is a point contact, for example, if there is a place where the outer wall of the inner tube is not in contact with the inner wall of the heat transfer area expansion tube, a heat transfer failure occurs, and a large heat transfer area can be used effectively. Disappear.
  • the outer contact portion 7 is formed to be point contact (length L2 is brought close to 0) so as to increase the heat transfer area.
  • the inner contact portion 6 is formed so as to have a contact length (the contact portion forms a surface in the entire double tube heat exchanger).
  • the outer contact portion 7 is formed to be point contact so as to increase the heat transfer area, and the inner contact portion 6 is Since the contact length is formed, it is possible to prevent contact failure between the outer wall of the inner tube and the inner wall of the heat transfer area expanding tube. For this reason, it can improve, without impairing heat-transfer performance.
  • FIG. 2 the double-pipe heat exchanger according to the first embodiment described above has an uneven shape (a bowl shape) in the outer flow path 5 formed between the outer tube 1 and the inner tube 2. It has a heat transfer area expansion tube 3 having a shape. As described in the first embodiment, the heat transfer area expansion pipe 3 is in contact with the heat transfer area expansion pipe inner wall and the inner pipe outer wall, and is in contact with the heat transfer area expansion pipe outer wall and the outer pipe inner wall. And the fin part 16 used as a side wall crosses the outer side flow path 5 in a pipe cross section.
  • the heat transfer area expansion tube 3 is inserted into the outer flow path 5. After that, the step of expanding the inner tube 2 or the step of contracting the outer tube 1 is performed.
  • the portion to be the fin portion 16 of the heat transfer area expansion tube 3 is perpendicular to the outer tube 1 and the inner tube 2, the inner contact portion is used when expanding or contracting the tube. 6 or a force applied to a portion to be the outer contact portion 7 is directly applied to the fin portion 16. For this reason, the fin part 16 bent in the unexpected form may be formed.
  • the portion that becomes the fin portion 16 is prevented from being vertical, and the load applied to the portion that becomes the fin portion 16 during expansion or contraction is reduced.
  • the fin part 16 is made to contact from an oblique direction with respect to an inner pipe outer wall and an outer pipe inner wall.
  • the outer contact portion 7 is a point contact as in the first embodiment described above
  • the outer wall of the inner tube and the inner wall of the heat transfer area expanding tube are in contact as shown in FIG.
  • the angle ⁇ at which the outer wall of the heat transfer area expanding tube and the inner wall of the outer tube come into contact with each other are set to be less than 90 °.
  • FIG. 3 is a diagram for explaining the lifting of the heat transfer area expansion tube 3.
  • a pressure more than necessary is applied to the inner tube 2 and the heat transfer area expansion tube 3 during a process such as expansion and contraction, deformation occurs in the inner contact portion 6 of the heat transfer area expansion tube 3.
  • an intermediate portion that should be contacted will be lifted.
  • the contact thermal resistance may increase and the heat transfer performance may be impaired.
  • the fin portion 16 is not only in contact with the outer wall of the inner tube and the inner wall of the outer tube from an oblique direction, but is also inserted into the outer channel 5 of the double-pipe heat exchanger.
  • the shape of the portion that becomes the fin portion 16 between the location that becomes the inner contact portion 6 (for the concave portion) and the location that becomes the outer contact portion 7 (the convex portion) is The shape is an arc.
  • the formed fin portion 16 is convex toward the inner tube 2 side in the direction of partial bending of the fin portion 16 due to expansion or contraction. Since the fin portion 16 is deformed to the inner tube 2 side by being formed so as to protrude toward the inner tube 2 side, the contact portion between the fin portion 16 and the inner tube 2 increases, and the inner contact portion 6 becomes longer. Become. Therefore, heat transfer from the inner tube 2 can be performed efficiently. For example, as shown in FIG. 2, the angle ⁇ ⁇ angle ⁇ , and the gap generated between the heat transfer area expansion pipe 3 and the inner pipe 2 is reduced. Therefore, for example, when the inner contact portion 6 is brazed, the brazing material easily enters. For this reason, the heat transfer from the inner tube 2 can be further efficiently performed. Further, as the angle ⁇ increases, the pressing force is weakened at the contact portion between the fin portion 16 and the outer tube 1, and an increase in the outer contact portion 7 can be suppressed.
  • the shape of the heat transfer area expansion tube 3 is an arc shape.
  • the shape is not limited to the arc shape, and the portion to be the fin portion 16 is a shape having a bent portion at least at one point. It is possible to exhibit the effect of the dispersion of the load and the prevention of lifting at the inner contact portion 6.
  • the above description is similarly established, for example, in a double-pipe heat exchanger in which the outer contact portion 7 is not a point contact, and the same effect can be exhibited.
  • FIG. FIG. 4 is a diagram showing a double-pipe heat exchanger according to Embodiment 3 of the present invention.
  • FIG. 4 shows a tube cross section similar to the AA ′ cross section in FIG. 1 described in the first embodiment.
  • the length L2 of the contact portion 7 is set to satisfy L1> L2.
  • L1 and L2 are L1 ⁇ L2
  • the end point of the inner contact portion 6 serves as a fulcrum. May be deformed.
  • the intermediate portion of the inner contact portion 6 may be lifted from the inner pipe 2, and the heat transfer performance may be impaired.
  • the outer contact portion 7 has a contact length when the tube cross section is viewed, and the outer tube 1 and the heat transfer area expansion tube 3 are connected. Even when an external force is applied so as to be in close contact, the force applied to the outer contact portion 7 is dispersed, and deformation of the tube can be prevented.
  • FIG. 5 is a diagram showing parameters set for shape analysis of the double-pipe heat exchanger according to Embodiment 3 of the present invention. As shown in FIG. 5, the number of convex portions (concave portions) of the heat transfer area expansion tube 3 is n, the outer diameter of the inner tube is dio, and the inner diameter of the outer tube is doi.
  • ⁇ 0 is an angle from the vertex of the convex portion of the heat transfer area expansion pipe 3 to the vertex of the next convex portion
  • ⁇ 1 is an angle that is a standard for forming the convex portion
  • ⁇ 2 is an angle that is a standard for forming the concave portion.
  • the length of contact between the inner tube 2 and the heat transfer area expansion tube 3 is L1
  • the length of contact between the outer tube 1 and the heat transfer area expansion tube 3 is L2.
  • ⁇ 0, ⁇ 1, ⁇ 2, ⁇ 1 ′, and ⁇ 2 ′ are expressed by equations (3) to (6).
  • the length L1 of the inner contact portion 6 and the length L2 of the outer contact portion 7 can be expressed by Expression (7) and Expression (8), respectively.
  • the length L1 of the inner contact portion 6 between the outer wall of the inner tube and the inner wall of the heat transfer area expansion tube, the inner wall of the outer tube and the heat transfer area Since the relationship between the outer wall 7 and the length L2 of the outer contact portion 7 is L1> L2, the external force applied to the outer contact portion 7 can be dispersed. Further, since the external force applied to the inner contact portion 6 and the external force applied to the outer contact portion 7 are substantially the same, excessive external force is dispersed without being applied only to the inner contact portion 6, thereby lifting the inner contact portion 6. Can be prevented. As described above, excessive deformation of each pipe can be prevented.
  • Embodiment 4 FIG. Although not particularly shown in the first to third embodiments described above, in order to further ensure the contact between the outer wall of the inner tube and the inner wall of the heat transfer area expansion tube, and the contact between the inner wall of the outer tube and the outer wall of the heat transfer area expansion tube, It is desirable to perform brazing with a brazing material 15 on each contact portion.
  • FIG. 6 is a diagram showing a brazing part according to the fourth embodiment of the present invention.
  • the brazing material 15 is applied, and brazing in the furnace is performed to melt the brazing material 15, and the contact portion is brazed. Attach.
  • the tube is made of aluminum or the like, an Al—Si based (aluminum-silicon based) alloy containing silicon in aluminum is used as the brazing material 15.
  • a clad material in which the brazing material 15 is clad (coated) in advance on the heat transfer area expansion tube 3 may be used.
  • Embodiment 5 FIG.
  • an example of a refrigeration cycle apparatus to which the double pipe heat exchanger described in the first to fourth embodiments is applied will be described.
  • the structure of four types of refrigeration cycle apparatuses will be described.
  • FIG. 7 is a diagram illustrating an example of the configuration of the refrigeration cycle apparatus according to the fifth embodiment.
  • the refrigerant circuit is configured by connecting the compressor 8, the condenser 9, the expansion valve 10, the evaporator 11, and the double pipe heat exchanger 12.
  • Compressor 8 sucks the refrigerant, compresses it, discharges it in a high temperature / high pressure state.
  • it may be configured by a compressor of a type that can control the number of revolutions by an inverter circuit or the like and adjust the discharge amount of the refrigerant.
  • the condenser 9 serving as a heat exchanger performs heat exchange between air supplied from a blower (not shown) and a refrigerant, for example, and condenses the refrigerant into a liquid refrigerant (condensates and liquefies). is there.
  • the expansion valve (pressure reducing valve, throttle device) 10 expands the refrigerant by reducing the pressure.
  • a flow rate control means such as an electronic expansion valve, but may be constituted by an expansion valve having a temperature sensing cylinder, a refrigerant flow rate adjustment means such as a capillary tube (capillary), or the like.
  • the evaporator 11 evaporates the refrigerant by heat exchange with air or the like to form a gas (gas) refrigerant (evaporate gas).
  • the double-pipe heat exchanger 12 in the refrigeration cycle apparatus of FIG. 7A performs heat exchange between the high-temperature and high-pressure refrigerant that has flowed out of the condenser 9 and the low-temperature and low-pressure refrigerant that has flowed out of the evaporator 11.
  • coolant in the condenser 9 can be raised by utilizing the double tube
  • capacitance at the time of heating can be improved and COP (value which remove
  • coolant which flowed out from the evaporator 11 can be gasified, it can prevent that a liquid refrigerant returns to the compressor 8.
  • the double-tube heat exchanger 12 in the refrigeration cycle apparatus of FIG. 7B exchanges heat between the high-pressure liquid refrigerant at the refrigerant outlet of the condenser 9 and the medium-pressure two-phase refrigerant that has passed through the flow control valve 13. I do. Then, the refrigerant that has undergone heat exchange and becomes medium-pressure gas refrigerant is bypassed to the suction-side piping of the compressor 8.
  • the refrigerant that has passed through the condenser 9 is branched before passing through the expansion valve 10 and is bypassed by using the double-tube heat exchanger 12.
  • the amount of refrigerant flowing downstream from the expansion valve 10 can be reduced. For this reason, pressure loss can be reduced and COP can be improved.
  • the double-tube heat exchanger 12 in the refrigeration cycle apparatus of FIG. 7C exchanges heat between the high-pressure liquid refrigerant at the refrigerant outlet of the condenser 9 and the medium-pressure two-phase refrigerant that has passed through the flow control valve 13. I do. And the refrigerant
  • the compressor 8 in the refrigeration cycle apparatus of FIG. 7 (c) is a multi-stage compressor capable of performing injection.
  • the refrigerant that has passed through the condenser 9 is branched before passing through the expansion valve 10 and is bypassed by using the double-pipe heat exchanger 12.
  • the amount of refrigerant flowing downstream from the expansion valve 10 can be reduced.
  • injection is possible in the middle part of the compressor section of the compressor 8 having a multi-stage configuration, input such as the discharge temperature of the compressor can be reduced, and COP can be improved.
  • the double-pipe heat exchanger 12 is used as a condenser. And let the fluid used as the heat exchange object of the refrigerant
  • coolant which flows through a refrigerant circuit be water, a brine, etc. (it demonstrates as water hereafter).
  • the pump 14 forms a flow of water and sends it to the double-pipe heat exchanger 12.
  • water is heated by heat exchange with the refrigerant.
  • the double-tube heat exchanger 12 is used as a condenser, but it can also be used as an evaporator.

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

Abstract

La présente invention se rapporte à un échangeur de chaleur à deux tubes qui comprend : un tube interne (2) à travers lequel passe un premier fluide ; un tube externe (1) qui présente un diamètre plus important que celui du tube interne (2) et qui recouvre le tube interne (2), un second fluide s'écoulant entre le tube interne (2) et le tube externe ; et un tube augmentant la surface de transfert de chaleur (3) qui est agencé dans l'espace situé entre le tube interne (2) et le tube externe (1) et qui a une forme de saillies et de creux et est configuré de telle manière que la longueur dans la direction circonférentielle du tube de la partie de contact intérieur (6) qui vient en contact avec la paroi externe du tube interne (2) soit plus longue que celle de la partie de contact extérieur (7) qui constitue la longueur dans la direction circonférentielle du tube de la partie qui vient en contact avec la paroi interne du tube externe (1) et de telle manière que les parties ailettes situées entre la partie de contact extérieur (7) et la partie de contact intérieur (6), qui traverse l'espace dans la section transversale de tube, vienne en contact avec la paroi externe du tube interne (2) et la paroi interne du tube externe (1) dans une direction diagonale.
PCT/JP2013/073688 2012-10-02 2013-09-03 Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération WO2014054370A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201380051921.4A CN104704311B (zh) 2012-10-02 2013-09-03 双管式换热器和制冷循环装置
EP13843545.8A EP2916091B1 (fr) 2012-10-02 2013-09-03 Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération
US14/432,630 US20150241132A1 (en) 2012-10-02 2013-09-03 Double pipe heat exchanger and refrigeration cycle device
JP2014539645A JP5944009B2 (ja) 2012-10-02 2013-09-03 二重管式熱交換器および冷凍サイクル装置
CN201320613402.XU CN203605763U (zh) 2012-10-02 2013-09-30 双层管式换热器及制冷循环装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JPPCT/JP2012/075530 2012-10-02
PCT/JP2012/075530 WO2014054117A1 (fr) 2012-10-02 2012-10-02 Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération

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WO2014054370A1 true WO2014054370A1 (fr) 2014-04-10

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PCT/JP2012/075530 WO2014054117A1 (fr) 2012-10-02 2012-10-02 Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération
PCT/JP2013/073688 WO2014054370A1 (fr) 2012-10-02 2013-09-03 Échangeur de chaleur à deux tubes et dispositif à cycle de réfrigération

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US (1) US20150241132A1 (fr)
EP (1) EP2916091B1 (fr)
JP (1) JP5944009B2 (fr)
CN (2) CN104704311B (fr)
WO (2) WO2014054117A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016102643A (ja) * 2014-11-18 2016-06-02 株式会社アタゴ製作所 熱交換器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016185963A1 (fr) * 2015-05-21 2016-11-24 日本碍子株式会社 Partie échangeur de chaleur
WO2017006389A1 (fr) * 2015-07-03 2017-01-12 三菱電機株式会社 Dispositif de pompe à chaleur
CN106032860A (zh) * 2015-09-02 2016-10-19 天津友大金属结构制造有限公司 一种远程运输用换热管
JP6471867B2 (ja) * 2015-10-06 2019-02-20 スズキ株式会社 排熱回収装置
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EP2916091B1 (fr) 2019-10-23
CN104704311A (zh) 2015-06-10
US20150241132A1 (en) 2015-08-27
CN203605763U (zh) 2014-05-21
CN104704311B (zh) 2017-03-01
EP2916091A4 (fr) 2016-08-10

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