WO2013183113A1 - Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant - Google Patents

Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant Download PDF

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Publication number
WO2013183113A1
WO2013183113A1 PCT/JP2012/064447 JP2012064447W WO2013183113A1 WO 2013183113 A1 WO2013183113 A1 WO 2013183113A1 JP 2012064447 W JP2012064447 W JP 2012064447W WO 2013183113 A1 WO2013183113 A1 WO 2013183113A1
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WO
WIPO (PCT)
Prior art keywords
plate
flow path
heat transfer
heat exchanger
fluid
Prior art date
Application number
PCT/JP2012/064447
Other languages
English (en)
Japanese (ja)
Inventor
伊東　大輔
岡崎　多佳志
相武 李
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 PCT/JP2012/064447 priority Critical patent/WO2013183113A1/fr
Priority to EP13800756.2A priority patent/EP2878909B1/fr
Priority to JP2014520001A priority patent/JP5940152B2/ja
Priority to CN201380029412.1A priority patent/CN104334994A/zh
Priority to US14/398,310 priority patent/US20150083379A1/en
Priority to PCT/JP2013/065456 priority patent/WO2013183629A1/fr
Priority to CN201320320010.4U priority patent/CN203561252U/zh
Publication of WO2013183113A1 publication Critical patent/WO2013183113A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips

Definitions

  • the present invention relates to a plate heat exchanger and a refrigeration cycle apparatus including the plate heat exchanger.
  • a plate heat exchanger In a plate heat exchanger, a plurality of heat transfer plates each having a plurality of rows of corrugated irregularities are stacked. As a conventional plate heat exchanger, the line connecting the tops of the corrugated peaks (or the bottom points of the valleys) of the heat transfer plate is arranged so as to intersect the adjacent heat transfer plate.
  • a helibone type has been proposed. Furthermore, an inner fin type heat exchanger has also been proposed in which the degree of freedom in designing the shape of the heat transfer plate is higher than that of the helibone type plate heat exchanger (see, for example, Patent Document 1).
  • Helicon type plate heat exchangers have the following problems.
  • the heat transfer plate since the heat transfer plate has a wave shape, it is difficult to form a leakage prevention function between the first fluid (for example, refrigerant) and the second fluid (for example, water). Since the hot water produced by the plate heat exchanger mounted on the water heater is used for bath water, it is necessary to prevent the refrigerant from leaking into this water. For this reason, if there is no leakage prevention function, combustible refrigerants such as CO2, hydrocarbons, and low GWP refrigerants that are high-pressure refrigerants cannot be used in the water heater.
  • combustible refrigerants such as CO2, hydrocarbons, and low GWP refrigerants that are high-pressure refrigerants cannot be used in the water heater.
  • the cross-sectional areas of the flow paths are substantially equal, when different fluids are flowed, the thermal resistance ratios of both are not equal, and the heat exchange efficiency is poor. Furthermore, the joint between adjacent plates is formed by wave point contact, and the joint area is small and easily broken.
  • the inner fin type heat exchanger as in Patent Document 1 has the following problems.
  • the inner fin type heat exchanger is difficult to use in a water heater because it has no leakage prevention function.
  • the shape of the inner fin is the same for the first flow path and the second flow path, and is not the optimum shape according to the flowing fluid, so the heat exchange efficiency is poor.
  • the inner fin has a specification that matches the required strength of one of the fluids, and the other fluid side is an inner fin having an excessive bonding area, which increases the cost.
  • Patent Document 2 discloses a first flow path plate and a second flow path plate each including a flow path within the thickness of the plate, and these flow path plates.
  • a structure provided with a partition plate for partitioning is disclosed.
  • the partition plate is a simple plate-like member and cannot be used for an embodiment using an inner fin.
  • Patent Document 3 As a heat exchanger provided with a corrosion prevention means, there is one disclosed in Patent Document 3.
  • the sub-plate which is a corrosion prevention means disclosed in Patent Document 3
  • Patent Document 3 since Patent Document 3 is a heat exchanger between a fluid flowing through a circular tube and a fluid flowing between fins, heat is exchanged only at the contact surface between the circular tube and the core plate. Heat exchange efficiency is low compared to exchangers.
  • JP 2003-185375 A page 5, FIG. 1
  • JP 2008-157544 A page 7, FIG. 2
  • JP 2009-133506 A page 12, FIG. 4
  • the present invention has been made in view of the above, and can improve the long-term reliability of the device by preventing fluid leakage while improving the heat exchange efficiency and being simple in structure and capable of being manufactured at low cost. It aims at providing a plate type heat exchanger.
  • the present invention has a plurality of heat transfer plates each having a flat heat transfer surface, and a first flow path and a second flow path are alternately formed between the pair of heat transfer plates.
  • a plate type heat exchanger provided with a plurality of inner fins disposed in the corresponding first flow path or second flow path, the inner fins disposed in the first flow path, The inner fin disposed in the second flow path is provided so as to have a different heat transfer area, and at least the first fluid or the second fluid flows between the pair of heat transfer plates.
  • a leakage prevention plate having holes formed therein is arranged.
  • the present invention it is possible to improve the long-term reliability of the apparatus by preventing fluid leakage while improving the heat exchange efficiency and having a simple structure and being inexpensively manufactured.
  • Embodiment 1 of this invention It is a disassembled perspective view which shows the offset fin type plate type heat exchanger in Embodiment 1 of this invention. It is a perspective view of an inner fin. It is a perspective view which shows the inner fin in a 1st flow path, and the inner fin in a 2nd flow path from diagonally upward. It is a top view which shows the inner fin in a 1st flow path, and the inner fin in a 2nd flow path. It is a figure explaining the characteristic regarding Embodiment 2 of this invention.
  • FIG. 1 is an exploded perspective view showing an offset fin type plate heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 2 is a perspective view of the inner fin.
  • FIG. 3 is a perspective view showing the inner fins in the first flow path and the inner fins in the second flow path obliquely from above, and
  • FIG. 4 shows the inner fins in the first flow path and the second flow paths. It is a top view which shows the inner fin.
  • the plate heat exchanger 1 includes at least a pair of side plates 3, a plurality of heat transfer plates 5 and leakage prevention plates 7 disposed between the side plates 3, and at least a pair of inner fins 9. ing.
  • the pair of side plates 3 plays a role of reinforcement, and has four inlets 11, a first fluid outlet 13, a second fluid inlet 15, and a second fluid outlet 17 at each of the four corners.
  • a passage hole is provided.
  • the first fluid inlet 11 is disposed at the upper corner of the left and right sides
  • the first fluid outlet 13 is disposed at the lower corner
  • the second fluid outlet is disposed at the lower corner of the left and right sides.
  • An inlet 15 is arranged, and an outlet 17 for the second fluid is arranged in the upper corner.
  • the flow direction of the first fluid is indicated by a symbol X
  • the flow direction of the second fluid is indicated by a symbol Y.
  • the heat transfer plate 5 is provided with a first fluid forward passage hole 11c, a first fluid return passage hole 13c, a second fluid forward passage hole 15c, and a second fluid return passage hole 17c as passage holes.
  • the leakage prevention plate 7 is provided with a first fluid forward passage hole 11d, a first fluid return passage hole 13d, a second fluid forward passage hole 15d, and a second fluid return passage hole 17d as passage holes.
  • Both the heat transfer plate 5 and the leakage prevention plate 7 are formed by processing a plate-like member having a substantially uniform thickness so that irregularities are formed by pressing or the like.
  • Each of the heat transfer plates 5 is a member having a flat heat transfer surface that forms the corresponding first flow path or second flow path.
  • Each of the heat transfer plates 5 is formed with a concave portion 5a and a convex portion 5b as a relative relationship.
  • the recess 5a includes the first fluid forward path hole 11c, the first fluid return path hole 13c, and Between these, the wide area which faces the inner fin 9 is occupied, and the convex part 5b occupies the peripheral part of the 2nd fluid outward path hole 15c and the 2nd fluid return path hole 17c.
  • the recess 5a includes the second fluid forward hole 15c, the second fluid return hole 17c, and the inner fin between them.
  • the convex portion 5b occupies a peripheral portion of the first fluid forward passage hole 11c and the first fluid return passage hole 13c.
  • Each of the leakage prevention plates 7 is a member disposed on the back side which is the back side of the flow path forming surface of the corresponding heat transfer plate 5. Moreover, the concave part 7a and the convex part 7b as a relative relationship are also formed in each of the leakage prevention plates 7. As shown in FIG. 1, each of the leakage prevention plates 7 has a surface having the same concavo-convex shape as the flow path forming surface side that is the surface of the corresponding heat transfer plate 5, and the back surface of the corresponding heat transfer plate 5. Is laminated. Accordingly, the corresponding heat transfer plate 5 and the leakage prevention plate 7 are closely aligned so that the back surface of the heat transfer plate 5 is flush with the surface of the leakage prevention plate 7.
  • the inner fins 9 are offset fins for promoting heat transfer arranged between the corresponding heat transfer plate 5 and the leakage prevention plate 7.
  • Each of the inner fins 9 has a substantially plate-like shape in which the width direction and the height direction are larger than the thickness direction, and as shown in FIG. Includes a structure extending so as to be repeated.
  • the inner fin 9 disposed in the first flow path and the inner fin 9 disposed in the second flow path have different heat transfer areas. Specifically, as shown in FIGS. 3 and 4, the inner fin 9 (9a) disposed in the first flow path and the inner fin 9 (9b) disposed in the second flow path are dimensioned. Are different from each other.
  • positioned at a 2nd flow path is comprised by the unevenness
  • the inner fin 9 in FIG. 1 has drawn the inner fin arrange
  • Each of the heat transfer plates 5 is brazed with the corresponding leakage prevention plate 7, and further, the corresponding heat transfer plate 5 and the leakage prevention plate 7 stacked so as to sandwich the corresponding inner fin 9 are brazed.
  • the leakage prevention plate is provided on the back surface of the heat transfer plate, for example, heat transfer forming a first flow path through which the first fluid flows. Even if the plate is damaged by corrosion, the first fluid is prevented from leaking into the second flow path due to the presence of the leakage prevention plate behind the plate and the presence of the brazing material between the heat transfer plate and the leakage prevention plate. be able to. Further, the presence of the brazing material can be expected to further suppress the progress of corrosion. Therefore, it is possible to improve the long-term reliability of the heat exchanger by preventing fluid leakage. Moreover, since the air layer is not included unlike the double wall structure in the helibone type plate heat exchanger, the amount of heat exchange is not reduced, and the use fluid can be expanded and the heat exchange performance can be improved.
  • the leakage prevention plate having a substantially flat shape is simply sandwiched between a pair of heat transfer plates having a substantially flat shape.
  • the heat exchanger can be manufactured at low cost without complicating the manufacture.
  • the thermal resistance ratio of refrigerant and water can be made equal.
  • the heat resistance ratio between the first fluid and the second fluid can be adjusted according to the physical properties of the flowing fluid, a heat exchanger with high heat exchange efficiency can be provided.
  • the leakage prevention plate is formed with a passage hole serving as a fluid inlet / outlet in a direction perpendicular to the flat heat transfer surface, thereby laminating a plurality of plates and using inner fins for both the water side and refrigerant side flow paths. Applicable to embodiments. Furthermore, since the leakage prevention plate has a passage hole serving as a fluid inlet / outlet in a direction perpendicular to the flat heat transfer surface, there is no need to form a distribution structure separately from the plate, and the flow path is formed thinly by stacking the plates. Combined with the effect, the heat exchanger can be made more compact.
  • the leakage prevention plate has a passage hole serving as a fluid inlet / outlet in a direction perpendicular to the flat heat transfer surface, the passage hole is formed when the first fluid and the second fluid are different from each other as described above. Can be produced in accordance with the characteristics of the fluid.
  • the hole diameter on the steam side is increased to reduce the increase in pressure loss, while the liquid pipe side is reduced in diameter to reduce heat.
  • the heat exchanger can be used efficiently in the two-phase region of steam and liquid with good heat transfer.
  • the heat exchanger has a structure in which a plurality of plates such as 100 or 200 are stacked and has a large number of flow paths
  • the distribution to each flow path is possible by adjusting the diameter of the passage holes.
  • the hole diameter can be adjusted without cost because it can be easily manufactured by a press.
  • the hole diameter can be easily adjusted, by reducing the hole diameter, the flow velocity of the fluid is increased, so that a large amount of fluid flows from the fluid inflow pipe to the flow path on the back side, or the hole diameter is increased. It is possible to easily realize that a large amount of fluid flows through the flow path close to the inflow pipe. Moreover, since the flow velocity can be reduced by increasing the hole diameter, corrosion (erosion) due to the flow velocity in the passage hole can be suppressed.
  • each of the first flow path and the second flow path is adjacent to the inner fin.
  • the temperature efficiency becomes higher than the configuration of Patent Document 2 described above.
  • the hole diameter of the passage hole can be increased, thereby suppressing the increase in pressure loss in the passage hole and the corrosion due to the increase in fluid speed. it can.
  • the inner fin and the flat heat transfer surface of the corresponding plate are joined face to face. Therefore, when the first fluid is a high pressure fluid and the second fluid is a low pressure fluid, an inner fin having a large contact area with the plate is provided in the first flow path through which the first fluid flows.
  • an inner fin with a small contact area with the plate in the second flow path it is possible to obtain a heat exchanger that can obtain sufficient strength required for each part, and can ensure strength without waste as a whole. it can.
  • the first embodiment it is possible to maintain good heat exchange efficiency by maintaining the same heat resistance ratio between the two fluids to be heat exchanged, and the structure is simple. Although it can be manufactured at low cost, the long-term reliability of the apparatus can be improved by preventing fluid leakage. Therefore, it is possible to use natural refrigerants such as CO2, flammable hydrocarbons, and low GWP refrigerants that could not be used because they have no refrigerant leakage prevention function. In addition, since the selection range of the fluid to be used increases, it is possible to select a refrigerant having a large latent heat, and it is possible to improve the heat exchange performance.
  • natural refrigerants such as CO2, flammable hydrocarbons, and low GWP refrigerants that could not be used because they have no refrigerant leakage prevention function.
  • the selection range of the fluid to be used increases, it is possible to select a refrigerant having a large latent heat, and it is possible to improve the heat exchange performance.
  • FIG. 5 the plate-type heat exchanger which concerns on Embodiment 2 of this invention is demonstrated.
  • the leakage prevention plate 7 that covers the entire heat transfer plate 5 is used.
  • the first fluid is used.
  • the leakage prevention plate 107 that covers only the area where the second fluid and the second fluid are adjacent to each other is used. That is, as the form of the leakage prevention plate 107, for example, as shown in FIG. 5B, the peripheral part (convex part 7b) of the first fluid forward passage hole 11d in the leakage prevention plate 7 of the first embodiment is used.
  • the form which was excised can be mentioned. Thereby, the material usage-amount of a leakage prevention plate can be reduced, and a heat exchanger can be manufactured cheaply.
  • Embodiment 3 As a third embodiment of the present invention, a mode in which the leakage prevention plates 7 and 107 are formed of a clad material will be described.
  • the leakage prevention plate is formed of a clad material, production efficiency can be improved.
  • the brazing material is sandwiched by itself in the manufacturing process, the brazing material may be displaced from the proper arrangement, resulting in poor bonding.
  • the production rate decreases.
  • brazing defects can be improved and the processing cost of the heat exchanger can be reduced.
  • Embodiment 4 FIG. As Embodiment 4 of the present invention, an embodiment in which a heat transfer plate, an inner fin, and a leakage prevention plate are integrated by brazing will be described.
  • a heat transfer plate, an inner fin, and a leakage prevention plate are integrated by brazing.
  • the adhesion of each part is improved, and a decrease in the heat transfer coefficient can be suppressed while assuming the presence of a leakage prevention plate.
  • a brazing material having a high thermal conductivity such as copper
  • the effect of suppressing a decrease in heat transfer coefficient is great. Since brazing provides good adhesion between components, the bonding strength is increased and a stable heat exchanger can be manufactured.
  • FIG. 5 of the present invention an aspect in which the thicknesses of the heat transfer plate and the leakage prevention plate are set to different dimensions will be described.
  • Making the leakage prevention plate thicker than the heat transfer plate is effective for the progress of corrosion and the strength improvement of the heat exchanger.
  • the plate thickness of the leakage prevention plate is made smaller than that of the heat transfer plate, the heat resistance of the leakage prevention plate can be reduced, so that the deterioration of the heat exchange performance can be suppressed and the material cost can be reduced.
  • the thickness of the leakage prevention plate may be selected according to desired conditions.
  • Embodiment 6 FIG.
  • a refrigeration cycle apparatus equipped with the plate heat exchanger according to any of the first to fifth embodiments described above will be given.
  • the compressor, the condenser (including the gas cooler), the expansion valve, and the evaporator are sequentially connected by the refrigerant pipe in the sixth embodiment, either or both of the condenser and the evaporator are The plate heat exchanger according to any one of Embodiments 1 to 5 is used.
  • a highly reliable refrigeration cycle apparatus can be obtained.
  • leakage prevention plate is exemplified as a single sheet, a plurality of leakage prevention plates may be stacked or formed of different materials.
  • material for the heat exchanger components metals such as stainless steel, copper, aluminum, and titanium, and synthetic resins can also be used.
  • the present invention can be used for many industrial and household equipment equipped with a plate heat exchanger, such as air conditioning, power generation, and food sterilization equipment.

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  • 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 qui maintient de façon satisfaisante l'efficacité de l'échange de chaleur, a une structure simple, peut être produit à peu de frais, et est apte à améliorer la fiabilité à long terme d'un dispositif en conséquence de la prévention des fuites de fluide. Un échangeur de chaleur du type à plaques (1) comprenant : une pluralité de plaques de transfert de chaleur (5, 5) ; une pluralité d'ailettes internes (9, 9) ayant un premier chemin d'écoulement et un second chemin d'écoulement formées en alternance entre chaque paire de plaques de transfert de chaleur (5, 5), et disposées dans le premier chemin d'écoulement ou dans le second chemin d'écoulement correspondant à chacune ; et une pluralité de plaques de prévention de fuite (7, 7). Des orifices de passage à travers lesquels du fluide est introduit sont prévus dans les plaques de prévention de fuite. Les ailettes internes (9) pour les premiers chemins d'écoulement et les ailettes internes (9) pour les seconds chemins d'écoulement sont prévues de sorte à avoir différentes surfaces de transfert de chaleur.
PCT/JP2012/064447 2012-06-05 2012-06-05 Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant WO2013183113A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
PCT/JP2012/064447 WO2013183113A1 (fr) 2012-06-05 2012-06-05 Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant
EP13800756.2A EP2878909B1 (fr) 2012-06-05 2013-06-04 Échangeur de chaleur du type plaque et dispositif à cycle de réfrigération le comprenant
JP2014520001A JP5940152B2 (ja) 2012-06-05 2013-06-04 プレート式熱交換器及びそれを備えた冷凍サイクル装置
CN201380029412.1A CN104334994A (zh) 2012-06-05 2013-06-04 板式热交换器以及具备其的冷冻循环装置
US14/398,310 US20150083379A1 (en) 2012-06-05 2013-06-04 Plate heat exchanger and refrigeration cycle system including the same
PCT/JP2013/065456 WO2013183629A1 (fr) 2012-06-05 2013-06-04 Échangeur de chaleur du type plaque et dispositif à cycle de réfrigération le comprenant
CN201320320010.4U CN203561252U (zh) 2012-06-05 2013-06-05 板式热交换器以及包括该板式热交换器的冷冻循环装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/064447 WO2013183113A1 (fr) 2012-06-05 2012-06-05 Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant

Publications (1)

Publication Number Publication Date
WO2013183113A1 true WO2013183113A1 (fr) 2013-12-12

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PCT/JP2012/064447 WO2013183113A1 (fr) 2012-06-05 2012-06-05 Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant
PCT/JP2013/065456 WO2013183629A1 (fr) 2012-06-05 2013-06-04 Échangeur de chaleur du type plaque et dispositif à cycle de réfrigération le comprenant

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PCT/JP2013/065456 WO2013183629A1 (fr) 2012-06-05 2013-06-04 Échangeur de chaleur du type plaque et dispositif à cycle de réfrigération le comprenant

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US (1) US20150083379A1 (fr)
EP (1) EP2878909B1 (fr)
CN (2) CN104334994A (fr)
WO (2) WO2013183113A1 (fr)

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JP5760124B1 (ja) * 2014-06-30 2015-08-05 株式会社Ihi 凝縮器及び洗浄装置
WO2016002811A1 (fr) * 2014-06-30 2016-01-07 株式会社Ihi Condenseur et dispositif de lavage
JP2016013536A (ja) * 2015-03-20 2016-01-28 株式会社Ihi 凝縮器及び洗浄装置
JP2017000996A (ja) * 2015-06-15 2017-01-05 株式会社Ihi 凝縮器及び洗浄装置
JPWO2014147804A1 (ja) * 2013-03-22 2017-02-16 三菱電機株式会社 プレート式熱交換器及びそれを備えた冷凍サイクル装置
WO2017141720A1 (fr) * 2016-02-19 2017-08-24 三菱重工サーマルシステムズ株式会社 Machine frigorifique et son procédé de commande

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JP6160385B2 (ja) * 2013-09-17 2017-07-12 株式会社デンソー 積層型熱交換器
CN105074375B (zh) * 2013-02-27 2018-05-15 株式会社电装 层叠型热交换器
CN105705284B (zh) * 2013-10-29 2019-05-31 舒瑞普国际股份公司 使用丝网印刷钎焊材料钎焊板式换热器的方法；利用该方法制造的板式换热器
DE102014217503A1 (de) 2014-09-02 2016-03-03 Illinois Tool Works Inc. Spülmaschine mit einer Flüssigkeits-Transportleitung
JP6525248B2 (ja) * 2015-02-18 2019-06-05 大日本印刷株式会社 熱交換器および熱交換器用プレートユニット
US20160377350A1 (en) * 2015-06-29 2016-12-29 Honeywell International Inc. Optimized plate fin heat exchanger for improved compliance to improve thermal life
CN111819415B (zh) * 2018-03-15 2022-09-27 三菱电机株式会社 板式热交换器、具备其的热泵装置、及具备热泵装置的热泵式供冷供暖供热水系统
JP6594598B1 (ja) * 2018-03-15 2019-10-23 三菱電機株式会社 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
DE112019001350B4 (de) * 2018-03-15 2024-06-13 Mitsubishi Electric Corporation Plattenwärmetauscher und diesen enthaltende Wärmepumpenvorrichtung
WO2020245876A1 (fr) * 2019-06-03 2020-12-10 三菱電機株式会社 Échangeur de chaleur du type à plaques et dispositif de transfert de chaleur
CN115210522A (zh) * 2020-03-05 2022-10-18 翰昂汽车零部件有限公司 板式热交换器
JP7301224B2 (ja) * 2020-05-19 2023-06-30 三菱電機株式会社 プレート式熱交換器、冷凍サイクル装置および伝熱装置

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