[go: up one dir, main page]

WO2007108240A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

Info

Publication number
WO2007108240A1
WO2007108240A1 PCT/JP2007/052036 JP2007052036W WO2007108240A1 WO 2007108240 A1 WO2007108240 A1 WO 2007108240A1 JP 2007052036 W JP2007052036 W JP 2007052036W WO 2007108240 A1 WO2007108240 A1 WO 2007108240A1
Authority
WO
WIPO (PCT)
Prior art keywords
pipe
heat exchanger
fluid
flow path
box
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2007/052036
Other languages
English (en)
Japanese (ja)
Inventor
Hiroki Hayashi
Kou Komori
Tomoichiro Tamura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of WO2007108240A1 publication Critical patent/WO2007108240A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—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 otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • 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

Definitions

  • the present invention relates to a heat exchanger for exchanging heat between a first fluid and a second fluid, and more particularly to a heat exchanger suitable for a heat pump type hot water heater.
  • JP 2003-314975 A page 4, FIG. 1
  • a pipe forming a first fluid passage is spirally wound around a container forming a second fluid passage.
  • a heat exchanger is listed. According to this heat exchanger, it is easy to take a long passage for the second fluid, and the wall surface of the container can be used as a heat transfer surface on which heat exchange is performed.
  • Japanese Patent Application Laid-Open No. 2005-24109 describes a box-type heat exchanger in which heat transfer tubes are arranged in a rectangular fluid passage. Since this heat exchanger directly transfers heat between the heat transfer tube wall and the fluid to be heated (for example, water), it can be miniaturized with high heat exchange efficiency.
  • the fluid flowing in the container does not directly contact the piping. Therefore, there is a problem that it is easily affected by heat radiation from the outside piping to the outside air.
  • An object of the present invention is to provide a heat exchanger that is excellent in heat exchange efficiency and can be further reduced in size.
  • the present invention includes a box body in which a first flow path having a rectangular outer shape that appears in a cross section perpendicular to the flow direction of the first fluid is formed,
  • a piping unit disposed in the first flow path and forming a second flow path through which a second fluid to be heat exchanged with the first fluid flows
  • a first pipe whose shape is adjusted so that the center of the pipe draws a serpentine first locus in the plane of the first reference plane which is a plane parallel to both the width direction and the flow direction of the first fluid;
  • a second pipe whose shape is adjusted so that the center of the pipe draws a meandering second locus within the plane of the second reference plane, which is a plane parallel to the first reference plane,
  • the positional relationship between the first pipe and the second pipe is determined so as to intersect at a plurality of locations along the flow direction of the first fluid.
  • the first pipe and the second pipe constituting the pipe unit each have a meandering shape in separate planes (first reference plane and second reference plane). Have.
  • the positional relationship between the first pipe and the second pipe is determined so as to intersect at a plurality of locations along the flow direction of the first fluid.
  • the first fluid is at the intersection of the first pipe and the second pipe. It flows through the first flow path so as to sew the space formed on the basis thereof.
  • it is possible to induce a three-dimensional flow of the first fluid that is, a complicated flow whose direction changes vertically and horizontally.
  • the temperature boundary layer can be prevented from reaching around the first pipe and the second pipe.
  • FIG. 1 is an overall perspective view of a heat exchanger according to an embodiment of the present invention.
  • FIG. 6A is a conceptual diagram illustrating the shape and arrangement of refrigerant tubes
  • FIG. 8A Action explanatory diagram showing the flow of water in a conventional heat exchanger
  • FIG. 8B Action explanatory diagram following FIG. 8A
  • FIG. 9A is an operation explanatory diagram showing the flow of water in the heat exchanger of the present embodiment.
  • FIG. 9B Action explanatory diagram following FIG. 9A
  • FIG. 10A Action explanatory diagram showing the flow of water in another conventional heat exchanger
  • FIG. 10B is an operation explanatory diagram showing the flow of water in the heat exchanger of the present embodiment.
  • a heat exchanger that is used in equipment such as a heat pump type hot water heater and performs heat exchange between water (first fluid) and a refrigerant (second fluid) such as carbon dioxide or alternative chlorofluorocarbon.
  • first fluid water
  • second fluid refrigerant
  • FIG. 1 is an overall perspective view of the heat exchanger of the present embodiment.
  • the heat exchanger 100 includes a box 14 and a piping unit 21.
  • the piping unit 21 includes two refrigerant pipes, a first refrigerant pipe 17 (first pipe) and a second refrigerant pipe 19 (second pipe), most of which are accommodated in the box body 14.
  • the box body 14 has a box body 12 and a lid 13.
  • An inlet pipe 15 for allowing water to flow into the box body 14 and an outlet pipe 16 for discharging water from the box body 14 are welded to the peripheral edge of the lid 13.
  • the box body 12 has four holes in total, two near the water inlet and two near the outlet, through which the piping unit 21 consisting of two refrigerant pipes 17 and 19 is placed in the box. Guided inside body 14.
  • FIG. 2 is an exploded plan view of the box shown in FIG. However, the refrigerant pipes 17 and 19 are omitted.
  • the internal space of the box 14 has a flat rectangular parallelepiped shape.
  • the sealed internal space constitutes the first flow path 14s through which water flows.
  • the first channel 14s has a rectangular outer shape that appears on the cross section perpendicular to the water flow direction FL.
  • the water flowing in from the inlet pipe 15 flows through the first flow path 14 s and flows out from the outlet pipe 16.
  • the box body 14 has a plurality of partition plates 25 arranged in its internal space.
  • the partition plates 25 are arranged in the box body 12 in parallel with each other at equal intervals in the width direction WL, and the first flow paths 14s in which the water flow direction FL is opposite by 180 degrees are alternately formed in the width direction WL. As shown, the internal space of the box 14 is partially partitioned. By these partition plates 25, the first flow path 14 s forms a so-called single-tain flow path (meandering flow path). The serpentine-type flow path is advantageous for saving useless space in the box 14.
  • the first flow path 14s is formed side by side in the height direction HL perpendicular to the water flow direction FL and the width direction WL.
  • the box body 12, the lid 13, and the partition plate 25 constituting the box body 14 can be made of a metal having good thermal conductivity, such as copper, copper alloy, SUS, aluminum alloy, or the like. .
  • the lid 13 and the partition plate 25 can be joined to the box body 12 by brazing or welding.
  • the refrigerant pipes 17 and 19 constituting the piping unit 21 are arranged in the first flow path 14s, and form second flow paths 17s and 19s through which a refrigerant to be heat-exchanged with water flows, respectively.
  • Such refrigerant pipes 17 and 19 are made of a metal having good thermal conductivity similar to that of the box body 14.
  • An internally grooved tube made can be used.
  • a leak detection tube 32 having a structure in which a small-diameter inner grooved tube 30 is covered with a large-diameter inner grooved tube 31 as shown in FIG.
  • the refrigerant can prevent the lubricating oil from entering the water.
  • the refrigerant pipes 17 and 19 are formed by bending a common leak detection pipe 32.
  • the refrigerant pipes 17 and 19 can be smooth inner pipes.
  • FIG. 3 shows an exploded plan view of the heat exchanger shown in FIG. 1.
  • FIG. 4 is a cross-sectional view taken along line AA in FIG. 3
  • FIG. 5 is a cross-sectional view taken along line BB in FIG. It has become.
  • each of the first refrigerant pipe 17 and the second refrigerant pipe 19 has a meandering shape with respect to the flow direction FL of water in the first flow path 14s, and one end of the first flow path 14s ( It is arranged over almost the entire area from the inlet pipe 15) to the other end (outlet pipe 16).
  • the first refrigerant pipe 17 and the second refrigerant pipe 19 are arranged so as to be overlapped in two upper and lower stages in the first flow path 14s.
  • the first refrigerant pipe 17 occupies the upper half space of the first flow path 14s
  • the second refrigerant pipe 19 occupies the lower half space of the first flow path 14s.
  • the width direction WL of the first flow path 14s is a predetermined one of the two opposite sides forming the rectangular outer shape of the first flow path 14s in a cross section perpendicular to the water flow direction FL.
  • the direction perpendicular to the width direction WL and the water flow direction FL can be defined as the height direction HL.
  • the virtual plane parallel to both the width direction WL and the water flow direction FL is defined as the first reference plane P1, and the virtual plane parallel to the first reference plane P1 is defined as the second reference plane P2. Is possible.
  • the stacking direction of the first refrigerant pipe 17 and the second refrigerant pipe 19 coincides with the height direction HL
  • the swinging direction of the refrigerant pipes 17 and 19 coincides with the width direction WL. If the dimension of the first flow path 14s with respect to the height direction HL is D, the first reference plane P1 is in the height direction HL.
  • the second reference plane P2 is D / 4 from the other wall 142k (bottom surface).
  • FIG. 6B shows a schematic plan view of a locus drawn by the center of the refrigerant pipe.
  • the shape of the first refrigerant pipe 17 is adjusted so that the center of the pipe draws a meandering first locus 17c in the plane of the first reference plane P1.
  • the shape of the second refrigerant pipe 19 is adjusted so that the center of the pipe draws a meandering second locus 19c in the plane of the second reference plane P2.
  • the first trajectory 17c and the second trajectory 19c each show a periodicity, specifically, a sinusoidal shape.
  • first refrigerant pipe 17 and the second refrigerant pipe 19 have a positional relationship with each other so as to intersect at a plurality of locations along the water flow direction FL when the directional force perpendicular to the first reference plane P1 is observed. It has been established. Water flows through the first flow path 14s so as to sew a space generated based on the intersection of the first refrigerant pipe 17 and the second refrigerant pipe 19.
  • the first refrigerant pipe 17 and the second refrigerant pipe 19 are arranged so that the intersecting positions of the two appear at equal intervals t along the water flow direction FL.
  • Each shape is adjusted and the positional relationship with each other is determined. That is, in the straight section of the first flow path 14s, the bent shape of the first refrigerant pipe 17 and the bent shape of the second refrigerant pipe 19 can be made common. In this way, the refrigerant tubes 17 and 19 can be easily manufactured. Further, since the entire structure is simplified, it becomes easy to optimize design conditions such as the bent shape of the refrigerant pipes 17 and 19 and the width of the first flow path 14s by computer simulation, for example.
  • the meandering phase of the first locus 17c described in FIGS. 6A and 6B and the meandering phase of the second locus 19c are shifted by a half cycle (180 degrees).
  • the positional relationship between the first refrigerant pipe 17 and the second refrigerant pipe 19 can be determined. In this way, the effect of inducing a three-dimensional water flow can be sufficiently obtained.
  • the meandering phase shift need not be strictly a half cycle. For example, about 180 ⁇ 10 degrees is included within a half cycle shift.
  • the refrigerant pipes 17 and 19 need to change the direction by 180 degrees.
  • the first refrigerant pipe 17 and the second refrigerant pipe 19 maintain a positional relationship that is shifted inward and outward from each other. The direction is changed 180 degrees while holding. In this way, it is possible to prevent the formation of a region where water flows easily (so-called dead water region).
  • one refrigerant tube is bent and bent so as to change the direction while contacting the wall surface of the box 14 forming the end of the first flow path 14s, and the other
  • the refrigerant pipe is bent and curved so that it passes through the inside with a smaller arc. In this way, it is possible to prevent a large dead water area from being formed in the reversal section where the direction of the first flow path 14s is reversed by 180 degrees.
  • the positional relationship between the first refrigerant pipe 17 and the second refrigerant pipe 19 is determined so as to be equal to the diameter (outer diameter) of the pipe. That is, the first refrigerant pipe 17 and the second refrigerant pipe 19 are in point contact with each other at the crossing positions. If the contact point between the first refrigerant pipe 17 and the second refrigerant pipe 19 is prevented from being connected in a linear manner, the flow path of the water can be prevented from being blocked, and the active three-dimensional flow can be prevented. The effect of preventing the increase in pressure loss can be expected.
  • the box body 14 is adjusted so that the height of the first flow path 14 s is approximately equal to the sum of the diameter of the first refrigerant pipe 17 and the diameter of the second refrigerant pipe 19. That is, as shown in FIGS. 3 and 4, the first refrigerant pipe 17 and the second refrigerant pipe 19 are in contact with the inner wall surfaces 14p, 14p, 141k, and 142k of the box body 14 in the upper, lower, left and right directions in the first flow path 14s. . That is, when the first flow path 14s is projected from one end to the other side in the flow direction FL, the inner wall surface on the opposite side of the box body 14 is blocked by the refrigerant pipes 17 and 19 so that it cannot be seen. ing.
  • the first refrigerant pipe 17 and the second refrigerant pipe 19 are each in contact with the inner wall surface 14p of the box body 14 in the width direction WL of the first flow path 14s. It has a meandering amplitude that enables heat transfer with the body 14. That is, the amplitude of the refrigerant pipes 17 and 19 is equal to the width of the first flow path 14s.
  • each refrigerant pipe 17, 19 may be in direct contact with the box body 14, or may be in indirect contact with another heat transfer section 27 as in the present embodiment.
  • the ratio of the total length of the refrigerant pipes 17 and 19 to the total length of the first flow path 14s can be increased, so that the heat exchanger 100 can be downsized. It is advantageous.
  • the other heat transfer section 27 that indirectly contact the refrigerant pipes 17 and 19 and the box body 14 include the box body 14 and the first refrigerant pipe 17, and the box body 14 and the second refrigerant pipe.
  • Such a brazed joint 27 is suitable because it can be easily formed as follows. Placing the refrigerant pipes 17 and 19 (piping unit 21) into the box while placing the brazing material previously formed into a sheet shape between the inner wall surfaces 14p, 14p, 141k and 142k of the box 14 and the refrigerant pipes 17 and 19 14 Place in. Then, the brazing material is melted and solidified in the heating furnace, and the box body 14 and the refrigerant pipes 17 and 19 are joined.
  • the first refrigerant pipe 17 and the second refrigerant pipe 19 may be joined by brazing or welding.
  • the box body 14 and / or the refrigerant pipes 17 and 19 may be made of a non-metallic material such as a resin.
  • a non-metallic material such as a resin.
  • Non-metallic materials represented by resins generally have the advantage of being lighter than metallic materials. Also, the resin is generally less expensive than the metal material.
  • An example of a nonmetallic material having good thermal conductivity is a resin containing a thermal conductive filler.
  • both the box body 14 and the refrigerant pipes 17 and 19 are made of a resin containing a heat conductive filler
  • an adhesive having an improved heat conductivity for example, a polymer adhesive kneaded with metal powder
  • the body 14 can be brought into contact with the refrigerant pipes 17 and 19.
  • the inner wall surface of the box 14 can be used as a heat transfer surface, so that the heat exchange efficiency can be increased.
  • the water flowing through the first flow path 14s and the high-temperature and high-pressure refrigerant flowing through the refrigerant pipes 17 and 19 flow opposite to each other. In this way, the efficiency of heat exchange between water and the refrigerant can be increased.
  • FIG. 8A consider a case where water flows straight along the longitudinal direction outside the refrigerant pipe 171.
  • the stirring action received from the refrigerant pipe 171 is small, the water as shown in FIG. 8B has a relatively large temperature ⁇ in the vicinity of the surface of the refrigerant pipe 171.
  • most of the surfaces of the refrigerant tubes 17 and 19 can contribute to heat transfer.
  • a piping unit 211 in which two refrigerant tubes 172 and 174 are spirally twisted as shown in FIG. 10A.
  • the two refrigerant tubes 172 since water tends to flow along the periphery of the piping unit 211, the two refrigerant tubes 172, The surface of 174 cannot necessarily be effectively used.
  • the first refrigerant pipe 17 and the second refrigerant pipe 19 create a moderately large space between them.
  • water forms a complex flow in that space. Since water flows while colliding with the surfaces of both the first refrigerant pipe 17 and the second refrigerant pipe 19, the surfaces of the first refrigerant pipe 17 and the second refrigerant pipe 19 can be effectively used as heat transfer surfaces.
  • the dead water area can be reduced. As the dead water area becomes smaller, the heat transfer area increases, so the heat exchange efficiency increases.
  • the partition plates 25 are arranged at equal intervals in the width direction WL, but the arrangement at equal intervals is not essential.
  • the arrangement interval of the partition plates 25 in the box body 14 can be adjusted so that the channel width on the downstream side is wider than the channel on the upstream side in the width direction WL.
  • metal ions such as calcium ions
  • scale is likely to deposit from around 60 ° C. If the flow path close to the water outlet 16 is designed to have a slightly wide opening, the increase in pressure loss due to scale deposition can be suppressed.
  • the heat exchanger according to the present invention has excellent heat exchange performance, and is useful as a heat exchanger for a heat pump water heater using a refrigerant. It can also be applied to heat exchangers that exchange heat between gases or liquids.

Landscapes

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

Abstract

L'invention concerne un échangeur de chaleur (100) comprenant un boîtier (14) formant une première conduite d'écoulement rectangulaire (14s) dans laquelle l'eau s'écoule, et une unité de tuyauteries (21) située dans la première conduite d'écoulement (14s). L'unité de tuyauteries (21) est composée d'un premier tuyau de substance refroidissante (17) et d'un deuxième tuyau de substance refroidissante (19). L'emplacement relatif du premier tuyau de substance refroidissante (17) et du second tuyau de substance refroidissante (19) est tel que les tuyaux se croisent à une pluralité de zones le long d'une direction d'écoulement d'eau (FL). L'eau s'écoule dans la première conduite d'écoulement (14s) pour circuler au travers d'un espace créé par le premier tuyau de substance refroidissante (17) et le deuxième tuyau de substance refroidissante (19).
PCT/JP2007/052036 2006-03-16 2007-02-06 Échangeur de chaleur Ceased WO2007108240A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006072442 2006-03-16
JP2006-072442 2006-03-16

Publications (1)

Publication Number Publication Date
WO2007108240A1 true WO2007108240A1 (fr) 2007-09-27

Family

ID=38522277

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/052036 Ceased WO2007108240A1 (fr) 2006-03-16 2007-02-06 Échangeur de chaleur

Country Status (1)

Country Link
WO (1) WO2007108240A1 (fr)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008007608A1 (de) * 2008-02-04 2009-08-06 Behr Gmbh & Co. Kg Wärmeübertrager mit Rohren
JP2009198043A (ja) * 2008-02-20 2009-09-03 Panasonic Corp 熱交換器
JP2010071583A (ja) * 2008-09-19 2010-04-02 Mitsubishi Electric Corp 熱交換器及びこれを備えた給湯器
CN101813425A (zh) * 2010-03-30 2010-08-25 上海交通大学 一种抛管换热器
JP2011094887A (ja) * 2009-10-30 2011-05-12 Fujitsu General Ltd 熱交換器
CN101538925B (zh) * 2008-03-18 2011-11-09 冯刚克 新型地辐射空调地面
JP2012107824A (ja) * 2010-11-18 2012-06-07 Furukawa Electric Co Ltd:The ２重管
WO2012136796A3 (fr) * 2011-04-08 2013-01-24 Bhp Billiton Aluminium Technologies Limited Eléments d'échange de chaleur destinés à être utilisés dans des cuves de traitement pyrométallurgique
WO2013105487A1 (fr) 2012-01-13 2013-07-18 パナソニック株式会社 Échangeur thermique
JP2014088985A (ja) * 2012-10-30 2014-05-15 Panasonic Corp 熱交換器及びそれを備えた給湯機
EP2706320A3 (fr) * 2012-09-10 2014-09-10 FTAS GmbH Echangeur thermique à tubes
JP2015021699A (ja) * 2013-07-23 2015-02-02 パナソニック株式会社 熱交換器
JP2015021619A (ja) * 2013-07-16 2015-02-02 パナソニック株式会社 熱交換器
CN104764292A (zh) * 2015-04-10 2015-07-08 佛山市美的清湖净水设备有限公司 用于净饮设备的速冷模块和具有它的净饮设备
DE102015103177A1 (de) * 2015-03-05 2016-09-08 Halla Visteon Climate Control Corporation Hochdruckkältemittelwärmeübertrager mit Mehrkanalflachrohren
JP2016186368A (ja) * 2015-03-27 2016-10-27 オリオン機械株式会社 温度調整装置
DE102016205353A1 (de) * 2016-03-31 2017-10-05 Mahle International Gmbh Stapelscheibenwärmetauscher
WO2021060984A1 (fr) * 2019-09-25 2021-04-01 Tanis Confectionery B.V. Dispositif et procédé de chauffage d'un produit de confiserie liquide
EP4199318A1 (fr) * 2021-12-17 2023-06-21 Valeo eAutomotive Germany GmbH Échangeur de chaleur d'un module électrique
JP2024143964A (ja) * 2023-03-29 2024-10-11 ダイキン工業株式会社 管継手用カバー

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE853461C (de) * 1951-03-22 1952-10-23 Arthur Fiedler Kaelteaustauscher
US4280556A (en) * 1980-01-22 1981-07-28 Suntime, Inc. Heat exchanger-tank assembly for hot water heating system
JP2005024109A (ja) * 2003-06-30 2005-01-27 Hitachi Cable Ltd 熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE853461C (de) * 1951-03-22 1952-10-23 Arthur Fiedler Kaelteaustauscher
US4280556A (en) * 1980-01-22 1981-07-28 Suntime, Inc. Heat exchanger-tank assembly for hot water heating system
JP2005024109A (ja) * 2003-06-30 2005-01-27 Hitachi Cable Ltd 熱交換器

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008007608A1 (de) * 2008-02-04 2009-08-06 Behr Gmbh & Co. Kg Wärmeübertrager mit Rohren
JP2009198043A (ja) * 2008-02-20 2009-09-03 Panasonic Corp 熱交換器
CN101538925B (zh) * 2008-03-18 2011-11-09 冯刚克 新型地辐射空调地面
JP2010071583A (ja) * 2008-09-19 2010-04-02 Mitsubishi Electric Corp 熱交換器及びこれを備えた給湯器
JP2011094887A (ja) * 2009-10-30 2011-05-12 Fujitsu General Ltd 熱交換器
CN101813425A (zh) * 2010-03-30 2010-08-25 上海交通大学 一种抛管换热器
JP2012107824A (ja) * 2010-11-18 2012-06-07 Furukawa Electric Co Ltd:The ２重管
WO2012136796A3 (fr) * 2011-04-08 2013-01-24 Bhp Billiton Aluminium Technologies Limited Eléments d'échange de chaleur destinés à être utilisés dans des cuves de traitement pyrométallurgique
CN103476969A (zh) * 2011-04-08 2013-12-25 Bhp比利顿铝技术有限公司 用于在火法冶金工艺容器中使用的热交换元件
WO2013105487A1 (fr) 2012-01-13 2013-07-18 パナソニック株式会社 Échangeur thermique
EP2706320A3 (fr) * 2012-09-10 2014-09-10 FTAS GmbH Echangeur thermique à tubes
JP2014088985A (ja) * 2012-10-30 2014-05-15 Panasonic Corp 熱交換器及びそれを備えた給湯機
JP2015021619A (ja) * 2013-07-16 2015-02-02 パナソニック株式会社 熱交換器
JP2015021699A (ja) * 2013-07-23 2015-02-02 パナソニック株式会社 熱交換器
DE102015103177A1 (de) * 2015-03-05 2016-09-08 Halla Visteon Climate Control Corporation Hochdruckkältemittelwärmeübertrager mit Mehrkanalflachrohren
JP2016186368A (ja) * 2015-03-27 2016-10-27 オリオン機械株式会社 温度調整装置
CN104764292A (zh) * 2015-04-10 2015-07-08 佛山市美的清湖净水设备有限公司 用于净饮设备的速冷模块和具有它的净饮设备
DE102016205353A1 (de) * 2016-03-31 2017-10-05 Mahle International Gmbh Stapelscheibenwärmetauscher
WO2021060984A1 (fr) * 2019-09-25 2021-04-01 Tanis Confectionery B.V. Dispositif et procédé de chauffage d'un produit de confiserie liquide
NL2023898B1 (en) * 2019-09-25 2021-05-25 Tanis Confectionery B V a device and method for heating a liquid confectionery product
EP4199318A1 (fr) * 2021-12-17 2023-06-21 Valeo eAutomotive Germany GmbH Échangeur de chaleur d'un module électrique
JP2024143964A (ja) * 2023-03-29 2024-10-11 ダイキン工業株式会社 管継手用カバー

Similar Documents

Publication Publication Date Title
WO2007108240A1 (fr) Échangeur de chaleur
CN203561252U (zh) 板式热交换器以及包括该板式热交换器的冷冻循环装置
WO2013105487A1 (fr) Échangeur thermique
JP6594598B1 (ja) プレート式熱交換器、プレート式熱交換器を備えたヒートポンプ装置、及び、ヒートポンプ装置を備えたヒートポンプ式暖房給湯システム
JP5206830B2 (ja) 熱交換器
JP6920450B2 (ja) 熱交換プレート、その熱交換プレートを用いたプレート・パッケージ、その熱交換プレートを用いた熱交換
JP2020012630A (ja) 熱交換器用伝熱プレート
US20110284193A1 (en) Heat exchanger
JP2013528773A (ja) 一体型熱伝導層を用いたコンパクトな板−フィン熱交換器
JPWO2018216245A1 (ja) プレート式熱交換器及びヒートポンプ式給湯システム
CN102620581B (zh) 一种换热器
JP5796222B2 (ja) 熱交換器
JP4936546B2 (ja) 熱交換器
JP2018054215A (ja) シェルアンドプレート式熱交換器
JP2009264643A (ja) 熱交換器
JP7244440B2 (ja) ヘッダープレートレス型熱交換器
JP2010255856A (ja) 熱交換器およびそれを用いたヒートポンプ給湯機
JP2013253710A (ja) 熱交換器およびこれを備えたヒートポンプ給湯機
JP6028452B2 (ja) 水熱交換器
JP2005024109A (ja) 熱交換器
JPH1114278A (ja) 熱交換器
JP3932877B2 (ja) 熱交換器
JP3641949B2 (ja) プレート式熱交換器
JP2013204861A (ja) 熱交換器
JP2003314975A (ja) 熱交換器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07713865

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 07713865

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP