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WO2007013439A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2007013439A1
WO2007013439A1 PCT/JP2006/314643 JP2006314643W WO2007013439A1 WO 2007013439 A1 WO2007013439 A1 WO 2007013439A1 JP 2006314643 W JP2006314643 W JP 2006314643W WO 2007013439 A1 WO2007013439 A1 WO 2007013439A1
Authority
WO
WIPO (PCT)
Prior art keywords
bent
heat exchanger
heat
heat exchange
peripheral surface
Prior art date
Application number
PCT/JP2006/314643
Other languages
English (en)
Japanese (ja)
Inventor
Hironaka Sasaki
Original Assignee
Showa Denko K.K.
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 Showa Denko K.K. filed Critical Showa Denko K.K.
Priority to DE112006001982T priority Critical patent/DE112006001982T5/de
Publication of WO2007013439A1 publication Critical patent/WO2007013439A1/fr

Links

Classifications

    • 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
    • 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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure

Definitions

  • the present invention relates to a heat exchanger, and more specifically, for example, a compressor, a gas cooler, an evaporator, a gas-liquid separator, a refrigerant that has come out of the gas cooler, and a refrigerant that has come out of the evaporator and has passed through the gas-liquid separator
  • a heat exchanger for example, a compressor, a gas cooler, an evaporator, a gas-liquid separator, a refrigerant that has come out of the gas cooler, and a refrigerant that has come out of the evaporator and has passed through the gas-liquid separator
  • An intermediate heat exchanger for exchanging heat and
  • the term “aluminum” includes aluminum alloys in addition to pure aluminum.
  • the term “supercritical refrigeration cycle” means a refrigeration cycle in which the refrigerant reaches a supercritical state exceeding the critical pressure on the high-pressure side. Means refrigerant used in the supercritical refrigeration cycle.
  • the supercritical refrigeration cycle has passed through the accumulator from the compressor, gas cooler, evaporator, accumulator as gas-liquid separator, expansion valve as decompressor, and high-temperature and high-pressure refrigerant and evaporator that came out of the gas cooler. It is equipped with an intermediate heat exchanger that exchanges heat with a low-temperature and low-pressure refrigerant.
  • the intermediate heat exchange in the supercritical refrigeration cycle is a heat exchanger that was not found in the conventional refrigeration cycle using a chlorofluorocarbon refrigerant, and the intermediate heat exchange is efficiently stored in the engine room of the automobile. However, it is currently considered to be placed in the engine room between the gas cooler and the evaporator.
  • a straight outer pipe As the heat exchange ⁇ used for the intermediate heat exchange ⁇ in the supercritical refrigeration cycle described above, a straight outer pipe, a straight inner pipe arranged concentrically at intervals in the outer pipe, and It is fixed to both ends of the heat exchange part, which is made up of fins that are integrally formed so as to extend in the length direction of the inner pipe, with a space in the circumferential direction on the outer peripheral surface of the inner pipe, and both the inner and outer pipes of the heat exchange part.
  • the gap between the outer and inner pipes of the heat exchange section is the first fluid passage and the inner pipe is the second fluid passage.
  • the refrigerant flowing through each passage portion can be efficiently mixed in both fluid passages.
  • the heat exchange efficiency between the flowing refrigerants may be insufficient.
  • Patent Document 1 International Publication No. 03Z085344 Pamphlet
  • An object of the present invention is to provide a heat exchange that can solve the above-described problems and can reduce the installation space.
  • the present invention has the following aspect power to achieve the above object.
  • the heat exchanging portion has a plurality of bent portions, and includes a bent portion bent in one plane including the axes of both the inner and outer tubes and the axes of the inner and outer tubes, and the above The heat exchange as described in 1) above, in which a bent part bent in another plane intersecting the plane is mixed ⁇
  • a compressor, a gas cooler, an evaporator, a gas-liquid separator, a pressure reducer, and a gas cooler force are provided, and an intermediate heat exchanger ⁇ that exchanges heat between the refrigerant that has come out and the refrigerant that has come out of the evaporator A refrigeration cycle using a supercritical refrigerant, wherein the intermediate heat exchange ⁇ is the heat exchange described in 1) above.
  • Coolant heating heat exchanger that exchanges heat between the high-temperature and high-pressure heat medium compressed by the compressor, outdoor heat exchanger, gas-liquid separator, decompressor, and engine power and engine coolant sent to the heater core And a heating cycle using a supercritical heat medium, wherein the heat exchange for heating the coolant is the heat exchange described in 1) above.
  • the engine coolant flows in the first fluid passage of the heat exchanger for heating the coolant, and the high-temperature and high-pressure heat medium compressed by the compressor also flows in the second fluid passage.
  • the heat exchange section is bent at at least one location, the total heat transfer between the fluids flowing in the first and second fluid passages of the heat exchange section. Even if the area is made as large as necessary to obtain the desired heat exchange performance, the linear spacing between the two connectors is shorter than the intermediate heat exchange described in Patent Document 1. Therefore, the linear length of the installation space for heat exchange can be made smaller than that of the heat exchanger described in Patent Document 1. For example, when it is mounted on an automobile, it can be bent into an arbitrary shape according to the empty space of the automobile, and the space in the engine room of the automobile can be used effectively.
  • the heat transfer area between the fluids flowing in the first and second fluid passages is increased, and the heat exchange efficiency is improved. Also, since the fins are formed integrally with the inner tube, the number of parts is reduced.
  • the inner tube is fixed to the outer tube, and the generation of abnormal noise due to vibration can be prevented.
  • the heat exchanger of 5) above When the heat exchanger of 5) above is mounted on a car, for example, it can be bent into any shape according to the free space of the car, making space in the engine room of the car effective. It can be used and the realization becomes high.
  • the tip end portions of some fins contact the inner peripheral surface of the bent inner portion and the bent outer portion of the outer tube. If the inner tube is sandwiched and fixed by the bent inner part and the bent outer part of the outer tube through the fins, the effect of preventing the generation of noise due to the inner tube being fixed to the outer tube is obtained. Further improvement.
  • the tip of one fin in the cross section of the bent portion of the heat exchanging portion, is in contact with the inner peripheral surface of the bent inner portion and the bent outer portion of the outer tube. If there is a fluid mixing part with a gap formed between the tip of the fin and the inner peripheral surface of the outer pipe on both sides in the circumferential direction, the axis of both the inner and outer pipes are included.
  • the bent portion bent in one plane and the bent portion bent in the other plane including the axis of both the inner and outer tubes and intersecting the plane are both the inner and outer tubes of the fluid mixing portion. The positions in the circumferential direction are different. Therefore, the fluid flowing in the first fluid passage is
  • the fluid mixing part In combination with the inertial force when passing through each bending part, the fluid mixing part will mix more efficiently, and the fluid flowing in both fluid passages due to the turbulent flow effect and the fluid temperature equalizing effect The effect of improving the heat exchange performance between the two becomes remarkable.
  • FIG. 1 shows the overall configuration of a first embodiment of a heat exchanger according to the present invention
  • FIGS. 2 to 4 show the configuration of the main part thereof.
  • Fig. 5 shows a supercritical refrigeration cycle using the heat exchanger of Fig. 1 as an intermediate heat exchanger.
  • the heat exchanger (1) has an outer tube (2) having a circular cross section and an inner tube having a circular cross section inserted concentrically into the outer tube (2) at intervals.
  • the heat exchange section (10) consisting of fins (4) provided on the outer peripheral surface of the pipe (3) and the inner pipe (3), and both pipes (2) and (3) of the heat exchange section (10)
  • With a fixed connector (5) and the heat exchanger (10), i.e. both pipes (2) (3) contain at least one axis, here the axis of both pipes (2) (3) It is bent at two points in one horizontal plane (P).
  • the bent part is indicated by (10A).
  • the outer tube (2) is also a metal, in this case, an aluminum extruded profile.
  • the inner tube (3) is also a metal, here an aluminum extruded profile, and has a plurality of fins (4) force circumferentially spaced on its outer peripheral surface and in the length direction of the inner tube (3). It is integrally formed to extend.
  • the linear part (10B) of the heat exchange part (10) excluding the bent part (10 A) there is a slight gap between the tip of the fin (4) and the outer peripheral surface of the outer pipe (2). Exists (see Figure 2). Both ends of the inner tube (3) protrude outward from the outer tube (2), and the fin (4) is cut off over the entire outer protruding portion (3a), and the finless portion (8) is removed.
  • a plurality of inner fins (9) extending over the entire length are integrally formed on the inner peripheral surface of the inner pipe (3) at intervals in the circumferential direction (see FIGS. 2 and 3).
  • the gap between the outer pipe (2) and the inner pipe (3) is the first fluid passage (6), and the inner pipe (3) is the second fluid passage (7). It has become.
  • the heat exchanging section (10) is formed by inserting a straight inner pipe (3) into a straight outer pipe (2) and then applying bending calorie. This bending cache is applied either before or after fixing the connector (5) to both pipes (2) and (3).
  • the outer pipe (2) is placed on the plane (P) with the bending center and the axis of the outer pipe (2). Slightly crushed in the direction of connecting.
  • the cross section of the bent portion (10A) of the heat exchange section (10) that is, the cross section orthogonal to the plane (P) (corresponding to the cross section along line B-B in FIG.
  • the tip of the fin (4) is in contact with the inner peripheral surface of the bent inner part (2a) and outer bent part (2b) of the outer pipe (2), and the inner bent part ( The inner pipe (3) is clamped and fixed via the fin (4) by the bent outer part (2b) and 2a).
  • the tips of some fins (4) are bent inner portions (2a) and outer bent portions (2) of the outer tube (2).
  • the gap between the tip of the fin (4) and the outer tube (2) inner circumferential surface is linear.
  • Part (10B ) Between the front end of the fin (4) and the outer peripheral surface of the outer tube (2), and the fluid mixing part (20) is formed there.
  • the connector (5) has a blocking force made of metal, here aluminum, and has a horizontal cylindrical part (5a) and a rectangular parallelepiped part connected to the upper end of the cylindrical part (5a). (5b).
  • the left connector (5) will be described.
  • an annular wall (11) is integrally formed so as to protrude rightward, so that the outer pipe fits into the end of the outer pipe (2).
  • a recess (12) is formed.
  • One end of the connector (5) opens to a portion surrounded by the annular wall (11) on the right end surface of the cylindrical portion (5a), and the other end opens to the upper surface of the rectangular parallelepiped portion (5b).
  • a flow path (13) communicating with the first fluid path (6) is formed.
  • a hole (14) is formed.
  • the left side portion of the finless portion (8) of the inner pipe (3) is inserted into the through hole (14).
  • the left end of the finless part (8) protrudes outward from the opening on the left end face side of the cylindrical part (5a) in the through hole (14), and the finless part (8) of the inner pipe (3)
  • the outer peripheral surface is joined to the peripheral edge of the left end opening of the through hole (14) in the cylindrical portion (5a). This joining is performed by brazing, here torch brazing.
  • An annular wall (15) is integrally formed on the left end surface of the cylindrical portion (5a) of the connector (5) around the through hole (14) so as to protrude leftward.
  • the left end of the fin-free part (8) of the inner pipe (3) protrudes to the left of the annular wall (15), and the part protruding from the annular wall (15) and the annular part of the fin-free part (8)
  • a union screw (16) is arranged to cover the wall (15).
  • the annular wall (15) is fitted into the large diameter part (17a) of the right end of the through hole (17) formed in the union screw (16), and the left end of the finless part (8) is the through hole (17). Is fitted into a small diameter portion (17b) connected to the right end large diameter portion (17a).
  • the right end of the union screw (16) is fitted in an annular recess (18) formed in the peripheral portion of the annular wall (15) on the left end surface of the cylindrical portion (5a), and the union screw (16) The right end of the outer peripheral surface of the cylinder and the inner peripheral surface of the recess (18) in the cylindrical portion (5a) It is joined. This joining is performed by brazing, here torch brazing.
  • the union screw (16) of one connector (5) is used to connect a pipe for supplying fluid into the second fluid passage (7), and the union screw (16 of the other connector (5) ) Is used to connect a pipe for draining fluid from the second fluid passage (7).
  • the connector (5) has a female screw hole (19) extending downward from the upper surface of the rectangular parallelepiped portion (5b).
  • the female screw hole (19) of one connector (5) is used to connect a piping nove for supplying fluid into the first fluid passage (6), and the female screw of the other connector (5).
  • the hole (19) is used to connect a piping pipe for discharging the fluid from the first fluid passage (6).
  • the right connector (5) is opposite to the left connector (5), and is fixed to the outer tube (2) and inner tube (3) in the same way as the left connector (5). ing.
  • FIG. 5 shows a supercritical refrigeration cycle using the heat exchange (l) described above as an intermediate heat exchange.
  • the supercritical refrigeration cycle uses CO as a supercritical refrigerant.
  • Refrigerant and evaporator from the compressor (21), gas cooler (22), evaporator (23), accumulator (24) as gas-liquid separator, expansion valve (25) as decompressor, and gas cooler (22) Provide intermediate heat exchange (l) to exchange heat with the refrigerant from (23)!
  • the supercritical refrigeration cycle is mounted on a vehicle such as an automobile as a car air conditioner.
  • Fig. 6 shows the same configuration as that of the heat exchanger (1) of the example except that the heat exchanger (1) of the first embodiment (1) (example) and a heat exchanger that is straight as a whole are provided.
  • the heat exchange performance with heat exchange is shown.
  • the substantial length of the heat exchanging portion (10) including the bent portion (10A) in the heat exchanger of the embodiment is equal to the linear length of the heat exchanging portion of the heat exchanger of the comparative example. From the results shown in Fig. 6, the heat exchange performance of the heat exchange (l) of the example is superior to that of the comparative example ⁇ . I understand.
  • FIG. 7 shows a second embodiment of the heat exchanger according to the present invention.
  • the heat exchange section (10) that is, both pipes (2) (3) are bent at at least one place, here three places.
  • the heat exchanging part (10) is the force bent in one plane (P1) (P2) (P3) including the axes of both pipes (2) (3).
  • the planes (P1), (P2), and (P3) cross each other.
  • the outer tube (2) has a bending center. It is slightly crushed in the direction connecting the axis of the outer tube (2). Then, along the cross section of the bent portion (10A) of the heat exchange section (10), that is, the cross section orthogonal to the plane (P1XP2XP3), the tip of the fin (4) of a part of the inner pipe (3) is The inner side (2a) and the outer side (2b) of the outer pipe (2) are in contact with the inner peripheral surface of the outer side (2a) and the outer side (2b). Thus, the inner tube (3) is clamped and fixed via the fin (4).
  • the end of some fins (4) are connected to the bent inner part (2a) and outer bent part of the outer tube (2) in the cross section of the bent part (10A) of the heat exchange part (10).
  • the gap between the tip of the fin (4) and the outer tube (2) inner circumferential surface is the fin in the linear portion (10B) on both sides in the circumferential direction of the portion that abuts (2b). It is larger than the space between the tip of (4) and the outer pipe (2) and the inner peripheral surface, and a fluid mixing section (20) is formed here.
  • the planes (P1), (P2), and (P3) cross each other, the position of the fluid mixing section (20) of each bending section (1 OA) is set to both pipes (2) (3 ) Is different in the circumferential direction.
  • FIG. And super 2 shows a heating cycle using a field heat medium.
  • the heating cycle uses CO as the supercritical heat medium
  • Heat exchanger (1X30) for heating the coolant that exchanges heat between the high-temperature and high-pressure heat medium compressed by the presser (50) and compressor (50) and the engine coolant sent from the engine (51) to the heater core (52)
  • An expansion valve (53) as a pressure reducer for reducing the pressure of the heat medium that has passed through the coolant heating heat exchanger (1X30), and an outdoor heat exchanger (54) for evaporating the heat medium depressurized by the expansion valve (53)
  • an accumulator (55) as a gas-liquid separator for separating the liquid in the heat medium sent from the outdoor heat exchanger (54) to the compressor (50).
  • the heating cycle is installed in a vehicle such as an automobile as a car air conditioner.
  • carbon dioxide is used as the supercritical refrigerant and supercritical heat medium, but is not limited to this, and ethylene, ethane, nitric oxide, and the like can also be used.
  • heat exchange is performed, for example, with a compressor, a gas cooler, an evaporator, a gas-liquid separator, and a gas cooler force.
  • ⁇ and CO intermediate heat exchange
  • FIG. 1 is an overall perspective view showing a first embodiment of a heat exchanger according to the present invention.
  • FIG. 2 is an enlarged sectional view taken along line AA in FIG.
  • FIG. 3 is an enlarged sectional view taken along line BB in FIG.
  • FIG. 4 is an enlarged sectional view taken along line CC in FIG.
  • V5 A diagram showing a supercritical refrigeration cycle using the heat exchanger of the first embodiment as an intermediate heat exchanger.
  • FIG. 7 is an overall perspective view showing a second embodiment of the heat exchange according to the present invention.
  • FIG. 8 is a diagram showing a heating cycle in which the heat exchangers of the first and second embodiments are used as a heat exchanger for heating a coolant.

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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

La présente invention concerne un échangeur de chaleur qui comprend une partie d’échange de chaleur (10) dotée d’un tube externe (2), d’un tube interne (3), et d’une pluralité d’ailettes (4) formées intégralement sur la surface périphérique externe du tube interne (3) s’étendant dans la direction longitudinale. La partie d’échange de chaleur (10) est courbée au moins dans une position. Dans la section transversale de la partie courbée (10A) de la partie d’échange de chaleur (10), les parties pointes d’une partie des ailettes (4) viennent au contact de la surface périphérique interne de la partie interne courbée (2a) et de la surface périphérique interne de la partie externe courbée (2b) du tube externe (2), et le tube interne (3) est maintenu fixement par la partie interne courbée (2a) et par la partie externe courbée (2b) du tube externe (2) à l’aide des ailettes (4). Dans la section transversale située au-dessus, les parties de mélange de fluide (20) présentant des dégagements entre les parties pointes des ailettes (4) et la surface périphérique interne du tube externe (2) sont formées sur les deux côtés périphériques de la portion où les parties pointes de la partie des ailettes (4) viennent au contact de la surface périphérique interne de la partie interne courbée (2a) et de la surface périphérique interne de la partie externe courbée (2b) du tube externe (2). Ainsi, on peut réduire l’espace d’installation destiné à l’échangeur de chaleur et augmenter sa performance en termes d’échange de chaleur.
PCT/JP2006/314643 2005-07-28 2006-07-25 Échangeur de chaleur WO2007013439A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112006001982T DE112006001982T5 (de) 2005-07-28 2006-07-25 Wärmetauscher

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-218206 2005-07-28
JP2005218206A JP2007032949A (ja) 2005-07-28 2005-07-28 熱交換器

Publications (1)

Publication Number Publication Date
WO2007013439A1 true WO2007013439A1 (fr) 2007-02-01

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PCT/JP2006/314643 WO2007013439A1 (fr) 2005-07-28 2006-07-25 Échangeur de chaleur

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JP (1) JP2007032949A (fr)
DE (1) DE112006001982T5 (fr)
WO (1) WO2007013439A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1985945A1 (fr) 2007-04-27 2008-10-29 Hutchinson Echangeur thermique interne pour circuit de climatisation de véhicule automobile, un tel circuit et procédé de raccordement de deux connecteurs à cet échangeur
EP2333472A1 (fr) 2009-12-10 2011-06-15 Hutchinson Echangeur thermique interne pour circuit de climatisation de véhicule automobile et un tel circuit
WO2012092454A1 (fr) * 2010-12-29 2012-07-05 Parker Hannifin Corporation Échangeur de chaleur interne
EP2706321A3 (fr) * 2012-09-05 2014-08-27 Hs R & A Co., Ltd. Tube double pour échange de chaleur
CN105387736A (zh) * 2015-12-17 2016-03-09 英特换热设备(浙江)有限公司 一种加强型螺旋管高效换热器
US20170045315A1 (en) * 2014-04-30 2017-02-16 Fmc Kongsberg Subsea As Subsea cooler
CN108225058A (zh) * 2017-12-27 2018-06-29 青岛海尔智能技术研发有限公司 空调换热器
EP3848660A1 (fr) 2020-01-09 2021-07-14 Hutchinson Raccordement étanche d'un connecteur a un échangeur thermique tubulaire coaxial
WO2021241422A1 (fr) * 2020-05-27 2021-12-02 株式会社デンソーエアシステムズ Échangeur de chaleur interne et procédé de production d'échangeur de chaleur interne

Families Citing this family (7)

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FR2915561A1 (fr) * 2007-04-27 2008-10-31 Hutchinson Sa Echangeur thermique interne pour circuit de climatisation de vehicule automobile, un tel circuit et procede de raccordement de deux connecteurs a cet echangeur
EP1985945A1 (fr) 2007-04-27 2008-10-29 Hutchinson Echangeur thermique interne pour circuit de climatisation de véhicule automobile, un tel circuit et procédé de raccordement de deux connecteurs à cet échangeur
EP2333472A1 (fr) 2009-12-10 2011-06-15 Hutchinson Echangeur thermique interne pour circuit de climatisation de véhicule automobile et un tel circuit
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CN103348208A (zh) * 2010-12-29 2013-10-09 康蒂泰克屈纳有限及两合公司 内置式热交换器
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US9513061B2 (en) 2012-09-05 2016-12-06 Hs R & A Co., Ltd. Dual pipe for heat exchange
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CN105387736A (zh) * 2015-12-17 2016-03-09 英特换热设备(浙江)有限公司 一种加强型螺旋管高效换热器
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FR3106201A1 (fr) 2020-01-09 2021-07-16 Hutchinson Raccordement etanche d’un connecteur a un echangeur thermique tubulaire coaxial
US11365939B2 (en) 2020-01-09 2022-06-21 Hutchinson Sealed connection of a connector to a coaxial tubular heat exchanger
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