WO2021002474A1 - 熱交換器 - Google Patents

熱交換器 Download PDF

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Publication number
WO2021002474A1
WO2021002474A1 PCT/JP2020/026313 JP2020026313W WO2021002474A1 WO 2021002474 A1 WO2021002474 A1 WO 2021002474A1 JP 2020026313 W JP2020026313 W JP 2020026313W WO 2021002474 A1 WO2021002474 A1 WO 2021002474A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
fin
offset
medium
flow path
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/JP2020/026313
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
威一郎 川村
坂井　耐事
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.)
T Rad Co Ltd
Original Assignee
T Rad 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 T Rad Co Ltd filed Critical T Rad Co Ltd
Priority to CN202080042618.8A priority Critical patent/CN113950605B/zh
Priority to JP2021529208A priority patent/JPWO2021002474A1/ja
Priority to DE112020003195.0T priority patent/DE112020003195T5/de
Publication of WO2021002474A1 publication Critical patent/WO2021002474A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • 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
    • F25B39/02—Evaporators
    • 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
    • F25B39/04—Condensers
    • 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
    • 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
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples

Definitions

  • a heat exchanger in which a plurality of dish-shaped plates are laminated, the first flow path and the second flow path are alternately arranged in the stacking direction, and offset fins are interposed in the first flow path.
  • a first flow path and a second flow path are formed between the laminated rectangular dish-shaped plates, and an inner fin is interposed in the first flow path. It is known that the entrance and exit of each flow path are provided at diagonal positions of the plate.
  • An example of the inner fin is an offset type, and in this offset type inner fin, the fluid flows and diffuses in the width direction of the fin through the gap of the offset part, but if it is not enough, the flow rate distribution Bias can occur, which can increase pressure loss.
  • an object of the present invention is to provide a heat exchanger having an offset type inner fin capable of making the flow rate distribution of the fluid uniform and reducing the pressure loss.
  • the first aspect of the present invention has a pair of long sides L facing each other and a pair of short sides M facing each other on the outer periphery, and the plane is formed in a rectangular dish shape. It has a large number of plates 3a, 3b in which a pair of first medium flow holes 1 are arranged diagonally and a second medium flow hole 2 is arranged in a second pair of diagonal positions, and each plate 3a, 3b is laminated, and the first flow path 4 of the first medium and the second flow path 5 of the second medium are alternately formed in the stacking direction, and the offset fin 6 is incorporated in the first flow path 4.
  • a heat exchanger in which the plates are liquid-tightly bonded and heat is exchanged between the two media.
  • the offset fins 6 are formed by bending a large number of waveforms 6a in which a metal plate advances in the short side M direction, and the adjacent waveforms 6a separated in the long side L direction are displaced from each other in the short side M direction. Then, the ridge line 6b of each waveform is arranged parallel to the long side L direction.
  • the aspect ratio b / a (aspect ratio) between the entrances and exits of the first medium of the plates 3a and 3b and the offset fins 6 is 0.12 ⁇ b / a ⁇ 0.33.
  • the fin pitch Pf of each waveform 6a of the offset fin 6 is 2 mm ⁇ Pf ⁇ 5 mm.
  • the heat exchanger is characterized in that the slit length SL of each waveform 6a of the offset fin 6 is 1 mm ⁇ SL ⁇ 3 mm.
  • the heat exchanger is an evaporator.
  • the heat exchanger according to claim 1 wherein the fin pitch Pf is 3 mm ⁇ Pf ⁇ 5 mm.
  • the heat exchanger is a condenser.
  • the invention of the heat exchanger according to claim 1 is an offset fin in a heat exchanger in which the aspect ratio b / a (aspect ratio) between the entrance and exit of the first medium is 0.12 ⁇ b / a ⁇ 0.33.
  • the fin pitch Pf of each waveform 6a of No. 6 is 2 mm ⁇ Pf ⁇ 5 mm, and the slit length SL of each waveform 6a of the offset fin 6 is 1 mm ⁇ SL ⁇ 3 mm.
  • the invention of the heat exchanger according to claim 2 is to provide an offset fin in an evaporator in which the aspect ratio b / a (aspect ratio) between the inlet and outlet of the first medium is 0.12 ⁇ b / a ⁇ 0.33.
  • the fin pitch Pf of each waveform is 3 mm ⁇ Pf ⁇ 5 mm, and the slit length SL of each waveform (6a) is 1 mm ⁇ SL ⁇ 3 mm.
  • the invention of the heat exchanger according to claim 3 is for offset fins in a condenser in which the aspect ratio b / a (aspect ratio) between the inlet and outlet of the first medium is 0.12 ⁇ b / a ⁇ 0.33.
  • the fin pitch Pf of each waveform is 2 mm ⁇ Pf ⁇ 3 mm, and the slit length SL of each waveform (6a) is 1 mm ⁇ SL ⁇ 3 mm.
  • FIG. 1 is a plan view (A) of a main part of the heat exchanger of the present invention, a perspective view (B) of the main part of the offset fin 6, and a CC arrow view (C) of (B).
  • FIG. 2 is an exploded perspective view of the heat exchanger.
  • FIG. 3 is a schematic cross-sectional view taken along the line III-III of FIG. 1 (A).
  • FIG. 4 shows the pressure drop ratio of the heat exchanger of the present invention, (A) shows a characteristic curve as an evaporator at each fin pitch Pf and a slit length SL, and (B) shows a characteristic curve as an evaporator. A characteristic curve showing the same pressure drop ratio.
  • FIG. 4 shows the pressure drop ratio of the heat exchanger of the present invention, (A) shows a characteristic curve as an evaporator at each fin pitch Pf and a slit length SL, and (B) shows a characteristic curve as an evaporator. A characteristic curve showing the same pressure drop ratio.
  • FIG. 5 shows the heat exchange amount ratio of the same heat exchanger, which is a characteristic curve for each fin pitch Pf and each slit length SL, (A) as a characteristic curve as an evaporator, and (B) as a condenser. Characteristic curve of.
  • FIG. 1A is a plan view of the heat exchanger plates 3a and 3b and the offset fins 6 interposed therein.
  • FIG. 1 (B) is an enlarged perspective view of the offset fin 6, and
  • FIG. 1 (C) is a view taken along the line CC of FIG. 1 (B).
  • FIG. 2 is an exploded perspective view of the heat exchanger.
  • FIG. 3 is a cross-sectional view taken along the line III-III of FIG. 1 (A). As shown in FIGS.
  • the core of this heat exchanger is composed of a laminated body of plates 3a and 3b, and the first flow path 4 and the second flow path 5 are formed every other one of the plates, and the first flow path 5 is formed.
  • An offset fin 6 is interposed in the flow path 4.
  • the plates 3a and 3b have a substantially square flat surface and are formed in a dish shape, a pair of first medium flow holes 1 are formed at the first diagonal position, and a pair of second medium flow holes 1 are formed at the second diagonal position. 2 is formed.
  • An annular bulge 9 is projected from the hole edge of the second medium flow hole 2 on the plate 3a side, and an annular bulge 9 is projected from the hole edge of the first medium flow hole 1 on the plate 3b side. Will be done.
  • the offset fin 6 interposed in the first flow path 4 is provided with an opening 10 so as to be aligned with the first medium flow hole 1 and the second medium flow hole 2 of each plate. Then, when they are laminated, a communication hole is formed between the adjacent plates. As shown in FIG. 2, a top plate 12 is fitted to the upper end of the core of this heat exchanger in the stacking direction via an end plate 15, and a pipe 13 is provided on the top plate 12. Then, they are arranged on the substrate 11, and each component is integrally brazed and fixed. Then, the first medium 7 circulates in each of the first flow paths 4 from the pipe 13 of one first medium, and flows out from the pipe 13 of the other first medium.
  • the second medium 8 circulates in each of the second flow paths 5 from the pipe 13 of one second medium, and flows out from the pipe 13 of the other second medium.
  • the first medium 7 is supplied with a refrigerant that changes into two phases of gas and liquid
  • cooling water is supplied as the second medium 8
  • heat exchange is performed between the two media.
  • the offset fin 6 interposed in the first flow path 4 can be formed of an aluminum material (including an alloy of aluminum) or the like, and as shown in FIGS. 1B and 1C, the short plate 3a is formed.
  • the waveform 6a is formed by being bent so that the wave travels at a constant fin pitch Pf in the direction of the side M.
  • An offset gap is formed in which the phase of the ridge line 6b of the waveform 6a is displaced by several pitches with respect to the direction of the long side L.
  • the offset gap interval can be, for example, about 1/4 of the fin pitch Pf.
  • the height H of the waveform 6a can be set to about 1/2 of the fin pitch Pf as an example, and the plate thickness of the offset fin 6 can be set to 0.1 mm to 0.3 mm as an example. ..
  • the present inventor circulates the offset fin 6 of the first flow path 4 under the conditions of the aspect ratio b / a between the entrance and exit of the heat exchanger, the fin pitch Pf of the offset fin 6, and the slit length SL thereof.
  • a of the aspect ratio b / a is the distance between the centers of the doorways measured parallel to the long side L of each plate 3 in FIG. 1 (A), and b is the center of the doorway measured parallel to the short side M.
  • the slit length SL is the length of the ridge line 6b of each waveform 6a in FIG. 1 (B).
  • the aspect ratio (b / a) is in the range of 0.12 ⁇ b / a ⁇ 0.33
  • the fin pitch Pf is in the range of 2 mm, 3 mm, 4 mm, and 5 mm
  • the slit length SL is in the range of 1 mm to 7 mm. did.
  • the first medium 7 flowing through the first flow path 4 is Freon
  • the second medium 8 flowing through the second flow path 5 is cooling water.
  • the pressure loss when a heat exchanger was used as the evaporator and the pressure loss when the heat exchanger was used as the condenser were measured for each offset fin 6.
  • the minimum value (lower limit) of the slit length SL is set to 1 mm based on the limit of press working of the offset fin.
  • the lower limit of the fin pitch Pf is set to 2 mm in consideration of the minimum offset gap of the offset fins.
  • the upper limit of the fin pitch Pf is set to 5 mm because if the Pf of the offset fin becomes too large, the pressure resistance of the inner fin between the plates of the heat exchanger cannot be sufficiently obtained. As a result, the following became clear. FIG.
  • FIG. 4A shows a pressure loss ratio (pressure loss ratio) when used as an evaporator.
  • the vertical axis is the pressure drop ratio
  • the horizontal axis is the slit length SL.
  • FIG. 4B shows a pressure loss ratio (pressure loss ratio) when used as a condenser.
  • the vertical axis, the horizontal axis, and how to take the reference are the same as in FIG. In both cases of FIGS. 4 (A) and 4 (B), the pressure drop ratio is small in the range where the slit length is short (SL is in the range of 1 mm to 3 mm).
  • FIG. 5 (A) shows the exchange heat amount ratio when used as an evaporator.
  • the vertical axis is the exchange heat amount ratio
  • the horizontal axis is the slit length SL.
  • FIG. 5 (B) shows the exchange heat amount ratio when used as a condenser.
  • the vertical axis, the horizontal axis, and how to take the reference are the same as those in FIG. 5 (A).
  • the aspect ratio b / a (aspect ratio) between the inlet and outlet of the first medium is 0.12 ⁇ b / a ⁇ 0.33. It is optimal that the slit length SL of the offset fin 6 is 1 mm ⁇ SL ⁇ 3 mm and the fin pitch Pf of the offset fin 6 is in the range of 3 mm ⁇ Pf ⁇ 5 mm.
  • the aspect ratio b / a (aspect ratio) between the inlet and outlet of the first medium is 0.12 ⁇ b / a ⁇ 0.33, and the slit of the offset fin 6 It is optimal that the length SL is 1 mm ⁇ SL ⁇ 3 mm and the fin pitch Pf of the offset fin 6 is in the range of 2 mm ⁇ Pf ⁇ 3 mm.
  • a heat exchanger other than a condenser for example, an oil cooler (the first medium is oil), etc., it is between the inlet and outlet of the first medium.
  • the aspect ratio b / a (aspect ratio) is 0.12 ⁇ b / a ⁇ 0.33, the slit length SL of the offset fin 6 is 1 mm ⁇ SL ⁇ 3 mm, and the fin pitch Pf of the offset fin 6 is 2 mm ⁇ Pf.
  • the range can be ⁇ 5 mm.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2020/026313 2019-07-02 2020-06-29 熱交換器 Ceased WO2021002474A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN202080042618.8A CN113950605B (zh) 2019-07-02 2020-06-29 热交换器
JP2021529208A JPWO2021002474A1 (https=) 2019-07-02 2020-06-29
DE112020003195.0T DE112020003195T5 (de) 2019-07-02 2020-06-29 Wärmetauscher

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-123984 2019-07-02
JP2019123984 2019-07-02

Publications (1)

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WO2021002474A1 true WO2021002474A1 (ja) 2021-01-07

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PCT/JP2020/026313 Ceased WO2021002474A1 (ja) 2019-07-02 2020-06-29 熱交換器

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JP (1) JPWO2021002474A1 (https=)
CN (1) CN113950605B (https=)
DE (1) DE112020003195T5 (https=)
WO (1) WO2021002474A1 (https=)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2025022466A1 (en) * 2023-07-22 2025-01-30 Falsafi Mehdi Plate-fin heat exchanger with optimal performance
WO2025126723A1 (ja) * 2023-12-15 2025-06-19 マレリ株式会社 フィン、熱交換器、及び熱交換器の製造方法
US20260016238A1 (en) * 2024-07-09 2026-01-15 Mahle International Gmbh Fin device for heat exchanger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005147572A (ja) * 2003-11-18 2005-06-09 Calsonic Kansei Corp 熱交換器用フィン
JP2007183071A (ja) * 2006-01-10 2007-07-19 Tokyo Bureizu Kk 高耐圧コンパクト熱交換器およびその製造法
WO2014132602A1 (ja) * 2013-02-27 2014-09-04 株式会社デンソー 積層型熱交換器
JP2016125686A (ja) * 2014-12-26 2016-07-11 株式会社マーレ フィルターシステムズ オイルクーラ
US20170284417A1 (en) * 2016-04-01 2017-10-05 Safran Aircraft Engines Output director vane for an aircraft turbine engine, with an improved lubricant cooling function using a heat conduction matrix housed in an inner duct of the vane

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JP4240136B2 (ja) * 2006-07-11 2009-03-18 株式会社デンソー 排気熱交換器
CN201433802Y (zh) * 2009-05-27 2010-03-31 无锡双翼汽车环保科技有限公司 板翅式铝质机油冷却器
KR20120002075A (ko) * 2010-06-30 2012-01-05 한라공조주식회사 판형 열교환기
JP5609339B2 (ja) * 2010-07-09 2014-10-22 株式会社デンソー オイルクーラ
WO2014048228A1 (zh) * 2012-09-26 2014-04-03 杭州三花研究院有限公司 换热器的翅片及换热器
JP6160385B2 (ja) * 2013-09-17 2017-07-12 株式会社デンソー 積層型熱交換器
JP5884055B2 (ja) * 2014-05-09 2016-03-15 パナソニックＩｐマネジメント株式会社 熱交換器および熱交換器用オフセットフィン

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005147572A (ja) * 2003-11-18 2005-06-09 Calsonic Kansei Corp 熱交換器用フィン
JP2007183071A (ja) * 2006-01-10 2007-07-19 Tokyo Bureizu Kk 高耐圧コンパクト熱交換器およびその製造法
WO2014132602A1 (ja) * 2013-02-27 2014-09-04 株式会社デンソー 積層型熱交換器
JP2016125686A (ja) * 2014-12-26 2016-07-11 株式会社マーレ フィルターシステムズ オイルクーラ
US20170284417A1 (en) * 2016-04-01 2017-10-05 Safran Aircraft Engines Output director vane for an aircraft turbine engine, with an improved lubricant cooling function using a heat conduction matrix housed in an inner duct of the vane

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2025022466A1 (en) * 2023-07-22 2025-01-30 Falsafi Mehdi Plate-fin heat exchanger with optimal performance
WO2025126723A1 (ja) * 2023-12-15 2025-06-19 マレリ株式会社 フィン、熱交換器、及び熱交換器の製造方法
US20260016238A1 (en) * 2024-07-09 2026-01-15 Mahle International Gmbh Fin device for heat exchanger

Also Published As

Publication number Publication date
CN113950605B (zh) 2026-02-06
JPWO2021002474A1 (https=) 2021-01-07
CN113950605A (zh) 2022-01-18
DE112020003195T5 (de) 2022-04-21

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