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WO2019159520A1 - Échangeur de chaleur pour réfrigérateur-congélateur - Google Patents

Échangeur de chaleur pour réfrigérateur-congélateur Download PDF

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Publication number
WO2019159520A1
WO2019159520A1 PCT/JP2018/045945 JP2018045945W WO2019159520A1 WO 2019159520 A1 WO2019159520 A1 WO 2019159520A1 JP 2018045945 W JP2018045945 W JP 2018045945W WO 2019159520 A1 WO2019159520 A1 WO 2019159520A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerator
fin
freezer
fins
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/JP2018/045945
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English (en)
Japanese (ja)
Inventor
上田　薫
幹根 笹崎
加奈 荻原
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.)
UACJ Corp
Original Assignee
UACJ Corp
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 UACJ Corp filed Critical UACJ Corp
Priority to CN201880085577.3A priority Critical patent/CN111556950A/zh
Publication of WO2019159520A1 publication Critical patent/WO2019159520A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • 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
    • F28F1/24—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 transversely
    • F28F1/32—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 transversely the means having portions engaging further tubular elements
    • 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

Definitions

  • the present invention relates to a heat exchanger for a refrigerator-freezer.
  • a serpentine heat exchanger is usually used as a heat exchanger mounted in a refrigerator-freezer.
  • the serpentine heat exchanger is composed of a plurality of plate fins arranged in a row in parallel at predetermined intervals, and a metal pipe through which one or a plurality of refrigerants passing through these fins are circulated.
  • a plurality of fin groups composed of a plurality of fins arranged in a row are arranged in a plurality of stages so that the air in the refrigerator, which is a fluid to be cooled, flows in the arrangement direction of the fin groups and sequentially passes through the plurality of fin groups. Be placed.
  • Patent Document 1 in order to suppress a decrease in heat exchange performance due to condensation, it is proposed to define a suitable fin interval and to provide a special coating layer on the surface of the fin.
  • the effect of the structure of patent document 1 cannot fully be acquired.
  • the present invention has been made in view of such background, and can improve the heat exchange performance per unit volume occupied by the heat exchanger, and heat exchange performance equivalent to the conventional heat exchange performance is required.
  • heat exchanger performance can be reduced compared to the conventional case, it is intended to provide a heat exchanger for a refrigerator / freezer that can be realized within the same occupied volume as before. is there.
  • One embodiment of the present invention includes a plurality of fin groups each including a plurality of fins arranged in a row at a predetermined interval in parallel, and a fluid to be cooled that circulates in the refrigerator-freezer through the plurality of fin groups.
  • the heat for a refrigerator-freezer having one or a plurality of metal pipes arranged in the X direction, which is the distribution direction, at a predetermined interval and arranged so as to pass through the fins in the fin group in a meandering manner.
  • the fin is made of an aluminum or aluminum alloy plate having a rectangular shape with a short side of 25 mm or less in the X direction, All of the shortest distances from the four corners of the rectangle to the outer peripheral surface of the metal pipe penetrating the fin are in the heat exchanger for a refrigerator / freezer in the range of 12.0 to 17.5 mm.
  • the refrigerator-freezer heat exchanger has a fin shape in which a short side length is regulated to be equal to or less than the specific value, and the positional relationship between the rectangular corner of the fin and the metal pipe is defined as the specific shape.
  • FIG. 3 is an explanatory diagram showing a dimensional relationship between fins of Example 1.
  • A Configuration of heat exchanger for refrigerator-freezer of Example 1
  • b Configuration of heat exchanger for refrigerator-freezer of Comparative Example 1
  • c Configuration of heat exchanger for refrigerator-freezer of Example 2
  • the rectangle In the refrigerator-freezer heat exchanger, a rectangular aluminum or aluminum alloy plate is used as the fin.
  • the rectangle generally means a quadrangle in which all four corners are right angles. However, when the angle of the corner is slightly deviated from the right angle, the corner apex is slightly rounded, Even when the side is slightly bent, all cases where it can be recognized as a rectangle are included.
  • the said fin is made into the rectangular shape which has the short side whose length (H) of the said X direction which is a distribution direction of the to-be-cooled fluid is 25 mm or less. It is generally considered that the fin shape improves heat exchange performance as the surface area increases. However, in a heat exchanger for a refrigerator-freezer, it has been found that if the dimension of the flow direction of the fluid to be cooled (X direction) is increased to some extent, the effect of improving the heat exchange performance can hardly be obtained. In particular, as proved in Example 1 described later, even if the short side length was reduced from the conventional 28 mm to 20 mm, no substantial decrease in the heat exchange performance was observed.
  • the short side length can be 20 mm to 28 mm.
  • the short side length is regulated to 25 mm or less.
  • the lower limit of the short side length is about 20 mm that exhibits the same performance as the conventional one. Although it is necessary to study from both aspects of heat exchange performance and miniaturization, the lower limit of the short side length is acceptable up to 18 mm considering at least manufacturing variations and other various variations.
  • the short side length is preferably set to 19 mm or more, more preferably 20 mm or more.
  • the fins have a shape in which the shortest distance (distance L1) from the four corners of the rectangle to the outer peripheral surface of the metal pipe penetrating the fins is in the range of 12.0 to 17.5 mm.
  • the heat exchange performance in the refrigerator-freezer can be optimized by regulating the distance L1 between the metal pipe and the corner of the fin within the predetermined range.
  • the distance L1 is less than 12 mm, sufficient heat exchange performance cannot be obtained, and when it exceeds 17.5 mm, further improvement in heat exchange performance cannot be expected. This means that when the distance L1 exceeds 17.5 mm, the fin shape is unnecessarily too large.
  • the metal pipe may be one, but two or more metal pipes may be penetrated by one fin.
  • the refrigerant flow rate can be increased as compared with the case where one metal pipe is used, and an improvement in heat exchange performance can be expected.
  • the fins are arranged so as to be aligned in a direction parallel to the long side of the rectangle of the fin so that the distance between them (the pipe interval L2) is in the range of 10 to 30 mm. It is preferable to set.
  • the pipe interval L2 is less than 10 mm, the fin area between the metal pipes is too small to improve the heat exchange performance.
  • it exceeds 30 mm the part does not contribute to the heat exchange sufficiently.
  • the area of the fin is preferably in the range of 480 to 750 mm 2 per metal pipe. That is, it is preferable that the value obtained by dividing the fin area by the number of metal pipes is in the above range.
  • the characteristics as a heat exchanger for a refrigerator / freezer can be improved by satisfying the requirements of the short side length and the distance L1 as described above after satisfying the requirements of the area. At least, by setting the fin area per metal pipe to 480 mm 2 or more, it is possible to ensure sufficient heat exchange from the viewpoint of area, while when it exceeds 750 mm 2 , heat exchange performance I cannot expect further improvement.
  • the fin is made of aluminum or an aluminum alloy plate. More specifically, a plate made of JIS A1050, JIS A1100, JIS A1200, JIS A7072 or the like can be used.
  • the fin has a thickness of 0.08 to 0.25 mm.
  • the heat dissipation efficiency that is, the “fin efficiency” that represents the ratio of the heat dissipation amount when the entire heat dissipation surface is the same temperature as the heat source and the actual heat dissipation amount decreases.
  • the fin thickness exceeds 0.25 mm, the effect of improving fin efficiency is saturated, and the overall weight may be increased.
  • the plurality of fin groups are arranged with an interval of 1 to 5 mm. If the distance between the fin groups (dimension C in FIGS. 1 to 3) is less than 1 mm, the leading edge effect may decrease, whereas if it exceeds 5 mm, the space between the fins is wasted. There is a risk.
  • the arrangement pitch of the fins in the fin group is 2.2 mm or more. Since the frost adheres to the surface of the fins when the heat exchanger for a refrigerator is used, it is difficult to secure a ventilation path if the arrangement pitch of the fins is too narrow. Therefore, as described above, the arrangement pitch of the fins is preferably 2.2 mm or more. On the other hand, if the fin pitch is too wide, the heat exchanger is increased in size. In the refrigerator-freezer heat exchanger, since the frost grows faster toward the upstream side, it is preferable to set the widest arrangement pitch of the fins in the most upstream fin group.
  • the metal pipe is preferably an internally grooved pipe having an outer diameter of 5 to 10 mm ⁇ and a groove on the inner peripheral surface.
  • the outer diameter of the metal pipe is less than 5 mm ⁇ , the flow rate of the refrigerant flowing through the inside cannot be secured sufficiently.
  • the heat exchange performance is lowered by reducing the fin area. There is a problem that the influence of.
  • the internally grooved pipe as the metal pipe, the heat exchange performance between the refrigerant and the metal pipe can be improved, and the characteristics as a heat exchanger can be further improved.
  • the metal pipe is preferably made of copper or copper alloy, or aluminum or aluminum alloy.
  • aluminum or aluminum alloy for metal piping include JIS A1050, JIS A1100, JIS A1200, and JIS A3003.
  • copper or copper alloy for metal piping include JIS H3300 C1220 and JIS H3300 C5010.
  • the refrigerant circulating in the metal pipe may be selected R134a, R600a, from one of CO 2.
  • R600a is the most common and has a low environmental load, and is suitable for use in a heat exchanger for a refrigerator-freezer.
  • cheaper R134a may be used, and CO 2 having a low environmental load may be used.
  • the metal pipe has a straight portion penetrating the fin and a U-shaped connecting portion for connecting a plurality of straight portions, a pipe radius r in an outer diameter dimension of the U-shaped connecting portion, It is preferable that the bending radius R on the U-shaped outer side of the U-shaped connecting portion has a relationship of R / r ⁇ 3.
  • R / r is less than 3
  • the metal pipe may be wrinkled or the like, which may adversely affect the fluidity of the refrigerant.
  • the heat exchanger 1 for a refrigerator / freezer of this example has a plurality of fin groups 2 including a plurality of fins 20 arranged in a row in parallel with each other at a predetermined interval.
  • the fin groups 2 are arranged at a predetermined interval C in the X direction, which is the flow direction of the fluid to be cooled that circulates in the refrigerator-freezer, and the fins 2 in the fin group 2 are sequentially penetrated to form a meandering form.
  • one or more metal pipes 3 are provided.
  • the fin 20 is made of an aluminum or aluminum alloy plate having a rectangular shape with a short side 21 having a length H of 25 mm or less in the X direction. All of the shortest distances L1 from the four corners of the rectangle to the outer peripheral surface of the metal pipe penetrating the fin 20 are in the range of 12.0 to 17.5 mm. Further details will be described below.
  • the refrigerator-freezer heat exchanger 1 of the present example has a plate fin made of a plate material having a material JIS A1050 and a thickness of 0.20 mm as the fin 20.
  • Each of the fins 20 has a rectangular shape in which the length H of the short side 21 is 20 mm and the length W of the long side 21 is 60 mm.
  • Each fin 20 has two through holes 25, and the metal pipes 3 are inserted through the through holes 25.
  • the inner diameter d of the through hole 25 in the fin 20 is 8 mm ⁇ , which is a dimension corresponding to the outer diameter of the metal pipe 3.
  • the shortest distances L1 from the four rectangular corners 211 of the fin 20 to the outer peripheral surface of the metal pipe 3 penetrating the fin 20 are all the same size, and all are 16.2 mm.
  • the interval L2 between two adjacent metal pipes 3 was 17 mm.
  • an inner grooved pipe made of JIS A3003, having an outer diameter ⁇ of 8 mm and having a groove on the inner peripheral surface was used.
  • the metal pipe 3 has a groove bottom portion with a thickness of 0.65 mm, a groove depth of 0.65 mm, and a groove number of 30. Since the area of the fin 20 is an area excluding the area occupied by the metal pipe 3, it is 550 mm 2 in this example.
  • the fin 20 and the metal pipe 3 are joined by expanding the metal pipe 3 with the metal pipe 3 having a slightly smaller outer diameter inserted through the through hole 25 of the fin 20.
  • the expansion of the metal pipe 3 employs either a mechanical pipe expansion method in which a mandrel (not shown) is pressed into the metal pipe 3 and moved, or a hydraulic pipe expansion method in which the metal pipe 3 is filled with oil and pressurized. Can be implemented.
  • the metal pipe 3 extends from the end 31 (FIG. 1) and connects the fin group 2 (g) on the most downstream side (uppermost side in FIG. 1 and FIG. 3A).
  • a plurality of stages on the downstream side sequentially through the plurality of U-shaped connecting portions 35.
  • the fin group 2 is meandering so as to pass through the fin group 2 and is disposed so as to pass through the fin group 2 (g) on the most downstream side (uppermost side in FIGS. 1 and 3 (a)) to reach the end 32.
  • the terminal 31 and the terminal 32 are connected to a compressor and other devices necessary for the refrigerator not shown.
  • the fin group 2 in this example has a seven-stage specification of fin groups 2 (a) to 2 (g) as shown in FIG. 3 (a).
  • the interval C between adjacent fin groups 2 was set to 3.0 mm. Therefore, the total dimension H2 in the X direction in which the seven-stage fin group 2 is arranged is 158 mm.
  • the arrangement pitch P of the fins 20 in each fin group 2 (FIG. 1) is the most upstream fin group 2 (a) in the flow direction of the fluid to be cooled (the lowest fin group in FIG. 3 (a)).
  • the second fin group 2 (b) from the upstream side becomes smaller in the order of the third fin group 2 (c) from the upstream side, and after that, all of them have the same size, but any arrangement pitch P is 2.2 mm. It was above.
  • Comparative Example 1 As a comparative example of Example 1, a heat exchanger 9 for a refrigerator / freezer having a configuration shown in FIG. For convenience of explanation, the same reference numerals are used for the same parts as in the first embodiment.
  • the refrigerator / refrigerator heat exchanger 9 of Comparative Example 1 is different from that of Example 1 in the dimensions of the fins 20 and the positional relationship with the metal pipe 3.
  • the fin 20 in the comparative example 1 has a rectangular shape in which the length H of the short side 21 is 28 mm and the length W of the long side 21 is 60 mm.
  • the shortest distances L1 (FIG. 2) from the four rectangular corners 211 of the fin 20 to the outer peripheral surface of the metal pipe 3 penetrating the fin 20 have the same dimensions, and all are 18.4 mm.
  • the area of the fin 20 is 790 mm 2 in this example.
  • fin group 2 it was set as seven steps like Example 1.
  • the interval C between adjacent fin groups 2 was set to 2.0 mm. Therefore, the total dimension H2 in the X direction in which the seven-stage fin group 2 is arranged is 208 mm.
  • Other configurations are the same as those in the first embodiment.
  • Example 2 As a modification of Example 1, a refrigerator-freezer heat exchanger 102 having the configuration shown in FIG. 4 was prepared.
  • the refrigerator-freezer heat exchanger 102 according to the second embodiment is configured to increase the number of stages of the fin group 2 to nine as compared with the first embodiment, thereby obtaining an occupied volume equivalent to that of the first comparative example.
  • the interval C between adjacent fin groups 2 was set to 3.0 mm. Therefore, the total dimension H2 in the X direction in which the nine-stage fin group 2 is arranged is 204 mm.
  • Other configurations are the same as those in the first embodiment.
  • Example 1 The heat exchangers of Example 1, Comparative Example 1 and Example 2 described above were incorporated into an actual refrigeration system, and an experiment was conducted to evaluate the performance. Specifically, an expansion valve, a compressor, and other necessary parts were connected to each heat exchanger to configure a known refrigeration system, and the refrigeration performance was evaluated under predetermined conditions.
  • the lower surface of the fin group 2 (b) on the lower side in FIG. 1 be an inlet for air that is a medium to be cooled in the heat exchanger, and let the upper side in FIG. And about the conditions (air side conditions) of the air introduce
  • the pressure on the inlet side of an expansion valve (not shown) is 1.826 MPa
  • the temperature on the inlet side of the expansion valve is 25 ° C.
  • the heat exchanger The pressure at the outlet was 0.485 MPa
  • the temperature at the outlet of the heat exchanger was ⁇ 8 ° C.
  • Example 1 As can be seen from Table 1, with respect to the heat exchanger of Example 1, the air side capacity was improved and the refrigerant side capacity was almost the same as the heat exchanger of Comparative Example 1. On the other hand, the total size of Example 1 is significantly smaller than that of Comparative Example 1. Then, when the evaluation value per unit volume was calculated in consideration of this dimensional difference, 1.30 or more, that is, an improvement of 30% or more was observed in any evaluation value with Comparative Example 1 as the reference (1). It was.
  • Embodiment 2 As described above, in Embodiment 1, it was found that the heat exchange performance improvement effect as described above can be obtained by changing the short side length H of the fin 20 from the conventional 28 mm to 20 mm. Based on this result, it is assumed that two refrigerant pipes are penetrated through a rectangular fin at an interval of 17 mm, the long side dimension W (width) of the fin is fixed to 60 mm, and the short side length H ( A simulation for obtaining the allowable range of H and L1 was performed by changing the height) and the shortest distance (distance L1) from the corner of the fin to the outer peripheral surface of the metal pipe. The number of stages of the fin group was seven, and the other configurations were the same as in Example 1. When the outer diameter of the refrigerant pipe is set to ⁇ 5 mm, the interval between the refrigerant pipes is set to 25 mm in order to arrange them at an equal distance.
  • the heat exchange performance is calculated by calculating the heat exchange capacity [W] from the temperature difference from the air temperature at the outlet when the refrigerant tube temperature is 5 ° C. and air at a predetermined temperature is introduced from the inlet. Used for evaluation. In addition, the ratio was evaluated based on the ratio when the measured value of the current heat exchanger was obtained and the measured value of the current heat exchanger was 1.

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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 pour réfrigérateur-congélateur, permettant de réduire la taille de l'échangeur de chaleur lorsque la performance d'échange de chaleur équivalente à la performance classique est requise, et étant apte à réaliser une amélioration des performances d'échange de chaleur avec le volume occupé équivalent à celui d'un dispositif classique lorsque la performance d'échange de chaleur doit être améliorée par rapport au volume classique. L'échangeur de chaleur pour réfrigérateur-congélateur comprend une pluralité de groupes d'ailettes (2), chaque groupe étant constitué d'une pluralité d'ailettes (20) agencées en une rangée et parallèles les unes par rapport aux autres à une distance prédéfinie les unes des autres. La pluralité de groupes d'ailettes (2) sont disposés à des intervalles prédéfinis dans une direction X qui est la direction d'écoulement du fluide à refroidir, circulant dans le réfrigérateur-congélateur. L'échangeur de chaleur comprend également un ou plusieurs tuyaux métalliques (3) qui sont agencés pour passer séquentiellement à travers les ailettes (20) dans les groupes d'ailettes (2) et pour avoir une forme en serpentin. L'ailette (20) est une plaque en aluminium ou en alliage d'aluminium ayant une forme rectangulaire dont les côtés courts ont une longueur inférieure ou égale à 25 mm dans la direction X. Toutes les distances les plus courtes des quatre coins (23) du rectangle à la surface périphérique externe des tuyaux métalliques (3) passant à travers les ailettes (20) sont dans la plage de 12,0 à 17,5 mm.
PCT/JP2018/045945 2018-02-13 2018-12-13 Échangeur de chaleur pour réfrigérateur-congélateur Ceased WO2019159520A1 (fr)

Priority Applications (1)

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CN201880085577.3A CN111556950A (zh) 2018-02-13 2018-12-13 冷冻冷藏库用热交换器

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JP2018-023402 2018-02-13
JP2018023402A JP2019138582A (ja) 2018-02-13 2018-02-13 冷凍冷蔵庫用熱交換器

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Publication number Priority date Publication date Assignee Title
EP4012315B1 (fr) * 2019-08-06 2025-01-22 Mitsubishi Electric Corporation Échangeur de chaleur et appareil à cycle de réfrigération
JP7614958B2 (ja) * 2021-06-29 2025-01-16 三菱電機株式会社 熱交換器および熱交換器の製造方法
JPWO2024128179A1 (fr) * 2022-12-16 2024-06-20

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WO2012014934A1 (fr) * 2010-07-27 2012-02-02 住友軽金属工業株式会社 Serpentin échangeur de chaleur pour climatiseur
WO2013069358A1 (fr) * 2011-11-09 2013-05-16 住友軽金属工業株式会社 Echangeur de chaleur en serpentin pour climatiseur
WO2014050418A1 (fr) * 2012-09-26 2014-04-03 株式会社Uacj Échangeur de chaleur à ailettes et à tubes pour climatiseur
CN107192290A (zh) * 2017-06-02 2017-09-22 江阴戴勒姆动力设备有限公司 多边形肋片多椭圆鳍片管换热元件

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JP2008215733A (ja) * 2007-03-05 2008-09-18 Kobelco & Materials Copper Tube Inc フィンアンドチューブ型熱交換器
JP5138408B2 (ja) * 2008-02-14 2013-02-06 住友軽金属工業株式会社 フィン・アンド・チューブ式熱交換器
JP5251237B2 (ja) * 2008-04-30 2013-07-31 ダイキン工業株式会社 フィンチューブ型熱交換器、これを備えた冷凍装置および給湯装置
JP2014059072A (ja) * 2012-09-14 2014-04-03 Sharp Corp 凝縮装置および冷凍冷蔵庫
CN105674630A (zh) * 2016-04-19 2016-06-15 合肥太通制冷科技有限公司 一种新型无侧板密翅卡位翅片蒸发器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010243067A (ja) * 2009-04-07 2010-10-28 Sumitomo Light Metal Ind Ltd 多段クロスフィンチューブ式熱交換器
WO2012014934A1 (fr) * 2010-07-27 2012-02-02 住友軽金属工業株式会社 Serpentin échangeur de chaleur pour climatiseur
WO2013069358A1 (fr) * 2011-11-09 2013-05-16 住友軽金属工業株式会社 Echangeur de chaleur en serpentin pour climatiseur
WO2014050418A1 (fr) * 2012-09-26 2014-04-03 株式会社Uacj Échangeur de chaleur à ailettes et à tubes pour climatiseur
CN107192290A (zh) * 2017-06-02 2017-09-22 江阴戴勒姆动力设备有限公司 多边形肋片多椭圆鳍片管换热元件

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