WO2022054963A1 - 熱交換器 - Google Patents

熱交換器 Download PDF

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Publication number
WO2022054963A1
WO2022054963A1 PCT/JP2021/034017 JP2021034017W WO2022054963A1 WO 2022054963 A1 WO2022054963 A1 WO 2022054963A1 JP 2021034017 W JP2021034017 W JP 2021034017W WO 2022054963 A1 WO2022054963 A1 WO 2022054963A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
heat exchange
heat exchanger
exchange medium
corrugated fin
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/JP2021/034017
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
卓也 文後
慶彦 岡▲崎▼
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 JP2022548383A priority Critical patent/JPWO2022054963A1/ja
Priority to DE112021004801.5T priority patent/DE112021004801T5/de
Priority to CN202180053671.2A priority patent/CN115997097A/zh
Publication of WO2022054963A1 publication Critical patent/WO2022054963A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10W—GENERIC PACKAGES, INTERCONNECTIONS, CONNECTORS OR OTHER CONSTRUCTIONAL DETAILS OF DEVICES COVERED BY CLASS H10
    • H10W40/00—Arrangements for thermal protection or thermal control
    • H10W40/40—Arrangements for thermal protection or thermal control involving heat exchange by flowing fluids
    • H10W40/47—Arrangements for thermal protection or thermal control involving heat exchange by flowing fluids by flowing liquids, e.g. forced water cooling
    • 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
    • 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
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • H—ELECTRICITY
    • H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10W—GENERIC PACKAGES, INTERCONNECTIONS, CONNECTORS OR OTHER CONSTRUCTIONAL DETAILS OF DEVICES COVERED BY CLASS H10
    • H10W40/00—Arrangements for thermal protection or thermal control
    • H10W40/20—Arrangements for cooling
    • H10W40/22—Arrangements for cooling characterised by their shape, e.g. having conical or cylindrical projections
    • H10W40/226—Arrangements for cooling characterised by their shape, e.g. having conical or cylindrical projections characterised by projecting parts, e.g. fins to increase surface area
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0028—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cooling heat generating elements, e.g. for cooling electronic components or electric devices
    • F28D2021/0029—Heat sinks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • heat exchangers that dissipate heat of heat exchange objects to heat exchange media especially heat exchangers that dissipate heat of heat exchange objects such as semiconductor elements.
  • heat exchange object such as a semiconductor element
  • heat is conducted from the heat exchange object to the core, and heat is transferred from the core to the heat exchange medium to raise the temperature of the heat exchange object.
  • Some are known to decline.
  • the heat exchange medium circulating inside the heat sink sequentially exchanges heat with the core according to the flow.
  • the present invention according to claim 1 has a pair of top plate plates 2 and bottom plate plates 3 facing apart from each other, and has a box shape including a peripheral wall portion 4 covering the outer periphery of the pair of plates 2 and 3.
  • the heat exchanger main body 1 of the above is formed, and an inner fin is interposed inside the heat exchanger main body 1.
  • the inner fin is a corrugated fin 5 in which a strip-shaped metal plate is folded back into a corrugated shape.
  • the ridge line portion 6a of each wave 6 of the corrugated fin 5 is joined to the pair of plates 2 and 3, and heat is exchanged with the opposite surface of the fin joint surface of at least one of the pair of plates 2 and 3.
  • the object 20 is attached, In a heat exchanger in which a heat exchange medium 21 flows inside the heat exchanger main body 1 along the wave ridge direction of the corrugated fins 5 and exchanges heat with the heat exchange object 20.
  • Concavo-convex stripes 10 are alternately formed on the rising surface 6b and the rising surface 6c of each wave 6 in the thickness direction of the strip-shaped metal plate.
  • Each of the uneven strips 10 has an inclination angle of 10 to 60 degrees with respect to the mainstream of the heat exchange medium 21, and the adjacent uneven strips 10 are arranged in the same direction as a heat exchanger.
  • the present invention according to claim 2 is the heat exchanger according to claim 1.
  • the heat exchanger is formed so that the uneven strips 10 move away from the heat exchange object 20 as the uneven strips 10 move from the upstream to the downstream of the mainstream of the heat exchange medium 21.
  • the present invention according to claim 3 is the heat exchanger according to any one of claims 1 and 2. Let A be the distance between the adjacent surfaces 6b and 6c of each wave 6 of the corrugated fin 5. When the height of the unevenness of the uneven strip 10 is Wh, It is a heat exchanger characterized by having a Wh / A value of 0.1 or more and 0.8 or less.
  • the present invention according to claim 4 is the heat exchanger according to claim 3.
  • the heat exchanger is characterized in that the value of Wh / A is 0.15 or more and 0.68 or less.
  • uneven strips 10 are alternately formed on the rising surface 6b and the rising surface 6c of each wave 6 of the corrugated fin 5 in which the strip-shaped metal plate is bent back in a wavy shape in the thickness direction of the strip-shaped metal plate.
  • Each of the uneven stripes 10 is formed and has an inclination angle of 10 to 60 degrees with respect to the mainstream of the heat exchange medium 21, and the adjacent uneven strips 10 are arranged in the same direction as a heat exchanger.
  • the heat exchange medium 21 in the groove portion of the uneven strip 10 arranged at an angle on the facing upper surface 6b and the rising surface 6c (flow path) of the heat exchange medium 21 is shown in FIG. 4 (A). As shown in FIG.
  • the heat exchange object 20 is attached to only one of the pair of plates 2 and 3 joined to the ridge portion 6a of the corrugated fin 5.
  • each uneven strip 10 is formed so as to move away from the heat exchange object 20 from the upstream to the downstream of the mainstream of the heat exchange medium 21.
  • the heat exchange medium that has not undergone heat exchange flows through the groove in the vicinity of the heat exchange target, and further improvement in heat exchange performance can be expected.
  • the distance between the adjacent surfaces 6b and 6c of each wave 6 of the corrugated fin 5 is set to A, and the unevenness thereof.
  • the value of Wh / A is 0.1 or more and 0.8 or less. With this configuration, it can be used in a range where the heat exchange performance is high even when the pressure loss is taken into consideration.
  • the invention according to claim 4 is the heat exchanger according to claim 3, wherein the Wh / A value is 0.15 or more and 0.68 or less. With this configuration, the heat exchange performance can be used in a range higher than that of the invention of claim 3.
  • FIG. 1 is an exploded perspective view showing the heat exchanger of the present invention.
  • FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 1 of the same heat exchanger.
  • FIG. 3 is a perspective view (A) of a main part showing the structure of the corrugated fin 5 of the first embodiment used for the core of the heat exchanger, a side view (B) of the corrugated fin 5, and a front view of the corrugated fin 5.
  • C) is an explanatory diagram of heat transfer of the heat exchange medium 21 circulating in the corrugated fin (concave and convex strip 10 downward slope) 5.
  • FIG. 5 is an explanatory diagram of heat transfer of the heat exchange medium 21 circulating in the corrugated fin 5 in which the pattern is not formed.
  • FIG. 6 is a heat dissipation characteristic diagram showing a comparison between the first embodiment by thermo-fluid analysis and the corrugated fin 5 having no pattern formed.
  • FIG. 7 is an explanatory diagram of heat transfer of the heat exchange medium 21 circulating in the corrugated fin 5 (concave and convex strip 10 rising to the right) of the second embodiment used for the core of the heat exchanger of the present invention.
  • FIG. 8 is a heat dissipation characteristic diagram showing a comparison with the corrugated fins 5 of the first embodiment and the second embodiment by thermal fluid analysis.
  • FIG. 9 is a diagram showing a comparison of the dependence of the degree of circulation N between the corrugated fins 5 used for the core of the heat exchanger of the present invention and the corrugated fins 5 having no pattern formed.
  • FIG. 10 is a cross-sectional view showing another embodiment of the heat exchanger of the present invention.
  • the heat exchanger of the present invention has an optimum structure for use as a heat sink or the like that dissipates heat from a heat exchange object such as a semiconductor element.
  • This heat exchanger has a pair of top plate plates 2 and bottom plate plates 3 facing apart from each other, and is a box-shaped heat exchanger composed of a peripheral wall portion 4 covering the outer periphery of the pair of plates 2 and 3.
  • the main body 1 is formed.
  • the top plate plate 2 covers the opening of the cup plate formed by the bottom plate plate 3 and the peripheral wall portion 4 integrally rising from the outer peripheral edge thereof. It fits.
  • the peripheral wall portion 4 may be separate from the bottom plate plate 3.
  • the inner fin is composed of a corrugated fin 5 in which a strip-shaped metal plate is folded back into a corrugated shape.
  • the corrugated fin 5 has a rising surface 6b and a rising surface 6c facing each other on one wave 6, and has a ridge portion 6a connecting them in a wavy shape. As shown in FIG. 2, the ridge line portion 6a of each wave 6 is joined to the pair of top plate plates 2 and bottom plate plates 3.
  • a heat exchange object 20 is attached to the outer surface (opposite surface of the fin joint surface) of at least one of the pair of plates 2 and 3 in the heat exchanger main body 1.
  • the heat exchange object 20 is attached to the outer surface of the top plate 2.
  • an inlet 22 into which the heat exchange medium 21 flows in and an outlet 23 through which the heat exchange medium 21 flows out are provided on the outer surface of the heat exchanger main body 1.
  • the heat exchange medium 21 circulates along the ridgeline direction of the wave ridgeline portion 6a of the corrugated fins 5 arranged inside the heat exchanger main body 1.
  • a refrigerant such as cooling water can be used as the heat exchange medium 21.
  • FIG. 5 is an explanatory diagram showing the heat transfer of the heat exchange medium 21 circulating in the core using the corrugated fin 5 having no pattern formed on the surfaces of the rising surface 6b and the rising surface 6c as a core.
  • the heat 24 generated from the heat exchange object 20 arranged in the upstream region of the flow of the heat exchange medium 21 is a corrugated connected to the heat exchange object 20 via a top plate 2 (not shown). Heat is transferred to the heat exchange medium 21 circulating in the vicinity of the ridge line portion 6a of the fin 5 (see FIG. 5B).
  • the heat-received medium 21a that has received heat 24 flows through the top plate 2 side as it is, and reaches the downstream region (point D in FIG. 5A) of the flow of the heat exchange medium 21. When it reaches the temperature, the temperature rises due to heat exchange, so that the action of receiving heat from the heat exchange object 20 arranged in the downstream region is reduced.
  • the unreceived heat medium 21b that has not received heat 24 flowing at a position away from the top plate 2 passes through the flow path in the corrugated fin 5 as it is and is discharged from the outlet 23.
  • a pattern of uneven stripes 10 in which convex portions 10a and concave portions 10b are alternately formed in a wavy shape in the thickness direction of the strip-shaped metal plate is formed.
  • the pattern of the uneven stripes 10 is formed on the rising surface 6b and the rising surface 6c except for the vicinity of the ridge line portion 6a of the corrugated fin 5.
  • the uneven strip 10 has an inclination angle ⁇ of 10 to 60 degrees with respect to the mainstream of the heat exchange medium 21, and the adjacent convex portions 10a and concave portions 10b are inclined in the same direction.
  • the inclination angles of the uneven strips 10 of the rising surface 6b and the rising surface 6c are also inclined in the same direction. Further, in this embodiment, as shown in FIG. 3, the inclination of the uneven strip 10 decreases in the lower right direction (moves away from the heat exchange object 20) as the mainstream of the heat exchange medium 21 goes from the upstream to the downstream. Is formed in. As shown in FIG. 4A, the heat exchange medium 21 in the flow path of the corrugated fin 5 receives heat 24 at the upstream position of the heat exchange medium 21 (point B in FIG. 4A) and has received heat. It becomes the medium 21a.
  • the heat-received medium 21a exchanges heat with the heat exchange target 20 while moving from the top plate 2 side to the bottom plate 3 side along the groove portions 10c formed on the surfaces 6b and 6c.
  • the groove portion 10c is separated from the groove portion 10c at the position (point D in FIG. 4A) of the ridge line portion 6a (the ridge line portion 6a connected to the bottom plate plate 3) where the inclined groove portion 10c disappears.
  • the unreceived heat medium 21b that has not exchanged heat with the heat exchange object 20 outside the groove portion 10c in the flow path flows into the groove portion 10c as shown in FIG. 4C, and is shown in FIG. 4 (C).
  • the heat-received medium 21a is replaced.
  • FIG. 6 shows a heat exchanger using a corrugated fin 5 having the pattern of the uneven streaks 10 of the present invention of FIG. The comparison of the thermal resistance with the heat exchanger using the above is shown.
  • the horizontal axis of the graph of FIG. 6 is the heat exchange object 20 arranged on the inlet side 20a (Inlet side), the intermediate portion 20b (Middle), and the outlet side 20c (Outlet side) of the heat exchange medium 21 in FIG.
  • each part is shown.
  • one heat exchange object 20 there are two heat-generating parts along the flow of the heat-exchange medium 21, and the six heat-generating parts are shown.
  • the vertical axis of the graph of FIG. 6 shows the thermal resistance (° C./W) at each site.
  • the experimental conditions are that the heat exchange medium 21 is water, the flow rate Vw is 6 L / min, the water inlet temperature Tw1 is 70 ° C., and the amount of heat input at each of the six locations is 300 W.
  • the heat exchanger using the corrugated fin 5 having the pattern of the uneven stripes 10 of the present invention is the corrugated fin 5 in which the pattern is not formed.
  • the heat dissipation characteristics are better in various places than the heat exchanger using. Further, when the thermal resistance on the inlet 22 side is 100, the ratio of the thermal resistance on the outlet 23 side uses the corrugated fin 5 having the pattern of the uneven stripes 10 of the present invention (the uneven stripes 10 have a downward-sloping inclined pattern).
  • the heat exchanger is 127.1 (the difference in ratio is 27.1%), while the heat exchanger using the corrugated fin 5 without a pattern is 134.8 (the difference in ratio is 34). 0.8%), and the heat exchanger of the present invention has a smaller rate of deterioration in heat dissipation characteristics on the outlet 23 side. Even if the above experimental conditions are changed, the absolute value indicated by the thermal resistance value in the graph of FIG.
  • FIG. 7 shows a second embodiment of the corrugated fin 5 used in the heat exchanger of the present invention, and describes the heat transfer of the heat exchange medium 21 circulating inside the corrugated fin 5.
  • This example differs from the example of FIG. 4 in that the pattern of the uneven stripes 10 is formed at an inclination angle rising to the right from the bottom plate plate 3 side to the top plate plate 2 side. This example will also be described under the condition that the heat exchange object is attached to the top plate 2 side. In this case, as shown in FIG.
  • FIG. 7A shows a heat exchanger using the corrugated fin 5 having the pattern of the first embodiment of FIG. 4 (the uneven stripe 10 is inclined downward to the right with respect to the mainstream direction of the heat exchange medium 21), and FIG. The comparison of the heat resistance with the heat exchanger using the corrugated fin 5 having the pattern of the second embodiment (the uneven stripe 10 is inclined upward to the right with respect to the mainstream direction of the heat exchange medium 21) is shown. ..
  • the description of the horizontal axis and the vertical axis of the graph is the same as in FIG. 6, and is omitted.
  • the experimental conditions are the same as in FIG. As shown in FIG. 8, even if the pattern-formed one of the second embodiment is used, the heat exchange medium 21 is circulated and the heat dissipation performance is improved as compared with the corrugated fin 5 in which the pattern is not formed. However, the heat dissipation characteristics are higher when the pattern of the first embodiment is used. Even if the above experimental conditions are changed, the absolute value indicated by the thermal resistance value in the graph of FIG. 8 changes, but the tendency indicated by the value does not change.
  • the present invention proposes to improve the heat dissipation characteristics of the entire heat exchanger by circulating the heat-received medium 21a and the non-heat-received medium 21b of the heat exchange medium 21.
  • increasing the degree of circulation improves the heat dissipation characteristics.
  • a decrease in the flow rate is also caused at the same time, which causes a decrease in heat dissipation characteristics.
  • the following items are examined to the extent that the above causes can be sufficiently avoided. In other words, the optimum value of the heat dissipation characteristic improvement allowance taking into account the pressure loss with respect to the degree of circulation was found by numerical calculation.
  • N (Vwave) / (Vcell)
  • Vwave and Vcell are as follows, respectively. It can be expressed by an expression.
  • Wp is the pitch of the pattern of the uneven stripes
  • Wh is the height of the pattern of the uneven stripes
  • ⁇ is the inclination angle of the pattern of the uneven stripes
  • A is the average width of one wave 6
  • B one wave.
  • the height of 6 and L are the flow path lengths.
  • FIGS. 9 (a) and 9 (b) show the results of confirming the dependence of the footprint heat transfer coefficient and the pressure loss on the degree of circulation (N), which are heat dissipation characteristic indexes, by thermo-fluid analysis.
  • FIG. 9C shows a heat dissipation characteristic index considering the pressure loss with the circulation degree (N) as a function.
  • the horizontal axes of (a), (b), and (c) in FIG. 9 each have a degree of circulation N.
  • FIG. 9A is the footprint heat of the present invention when the heat transfer coefficient of the heat exchanger using the corrugated fin 5 having no pattern (hereinafter referred to as a comparison target) is 1.
  • a comparison target Take the transmission rate ratio (arb.unit).
  • the vertical axis of FIG. 9B takes a pressure drop index (arb.unit).
  • the vertical axis of FIG. 9C takes a heat dissipation characteristic index (arb.unit) in consideration of pressure loss.
  • the solid line of each graph is the present invention, and the alternate long and short dash line indicates the comparison target.
  • the experimental conditions are the same as in FIG. In FIG.
  • the increase rate of the pressure loss exceeds the increase rate of the heat dissipation characteristic, so that the heat dissipation characteristic index considering the pressure loss decreases. It can be inferred that this is because the footprint heat transfer coefficient decreases due to the decrease in the flow rate due to the increase in pressure loss. From the above, it was found that the improvement of heat dissipation characteristics in consideration of the pressure loss shows the maximum value when the circulation degree (N) is 0.3. As can be seen from FIG. 9 (C), the circulation degree (N) has a heat dissipation characteristic value of 50% or more of the maximum value in the range of the equation 5.

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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)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
PCT/JP2021/034017 2020-09-14 2021-09-09 熱交換器 Ceased WO2022054963A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2022548383A JPWO2022054963A1 (https=) 2020-09-14 2021-09-09
DE112021004801.5T DE112021004801T5 (de) 2020-09-14 2021-09-09 Wärmetauscher
CN202180053671.2A CN115997097A (zh) 2020-09-14 2021-09-09 热交换器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020154190 2020-09-14
JP2020-154190 2020-09-14

Publications (1)

Publication Number Publication Date
WO2022054963A1 true WO2022054963A1 (ja) 2022-03-17

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PCT/JP2021/034017 Ceased WO2022054963A1 (ja) 2020-09-14 2021-09-09 熱交換器

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JP (1) JPWO2022054963A1 (https=)
CN (1) CN115997097A (https=)
DE (1) DE112021004801T5 (https=)
WO (1) WO2022054963A1 (https=)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003343985A (ja) * 2002-05-27 2003-12-03 Komatsu Electronics Inc プレート状熱交換器
JP2016003778A (ja) * 2014-06-13 2016-01-12 富士電機株式会社 ループ型サーモサイフォン
WO2016043340A1 (ja) * 2014-09-19 2016-03-24 株式会社ティラド 熱交換器用コルゲートフィン
JP2019219139A (ja) * 2018-06-22 2019-12-26 株式会社ティラド 熱交換器用コルゲートフィン

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1148772B1 (en) * 2000-04-19 2009-12-23 Thermal Form & Function Inc. Cold plate utilizing fin with evaporating refrigerant
EP1918668B1 (de) * 2006-10-27 2010-06-02 Behr GmbH & Co. KG Vorrichtung zur Aufnahme eines Fluids mittels Kapillarkräften und Verfahren zur Herstellung der Vorrichtung
JP2010203694A (ja) * 2009-03-04 2010-09-16 Showa Denko Kk 液冷式冷却装置
JP2011091301A (ja) * 2009-10-26 2011-05-06 Toyota Industries Corp 液冷式冷却装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003343985A (ja) * 2002-05-27 2003-12-03 Komatsu Electronics Inc プレート状熱交換器
JP2016003778A (ja) * 2014-06-13 2016-01-12 富士電機株式会社 ループ型サーモサイフォン
WO2016043340A1 (ja) * 2014-09-19 2016-03-24 株式会社ティラド 熱交換器用コルゲートフィン
JP2019219139A (ja) * 2018-06-22 2019-12-26 株式会社ティラド 熱交換器用コルゲートフィン

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CN115997097A (zh) 2023-04-21
JPWO2022054963A1 (https=) 2022-03-17
DE112021004801T5 (de) 2023-07-27

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