EP2336701A2 - Rippe mit niedrigem Druckverlust mit selektiver Mikrooberflächenverbesserung - Google Patents

Rippe mit niedrigem Druckverlust mit selektiver Mikrooberflächenverbesserung Download PDF

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Publication number
EP2336701A2
EP2336701A2 EP10193609A EP10193609A EP2336701A2 EP 2336701 A2 EP2336701 A2 EP 2336701A2 EP 10193609 A EP10193609 A EP 10193609A EP 10193609 A EP10193609 A EP 10193609A EP 2336701 A2 EP2336701 A2 EP 2336701A2
Authority
EP
European Patent Office
Prior art keywords
spoilers
air
long
fins
legs
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.)
Granted
Application number
EP10193609A
Other languages
English (en)
French (fr)
Other versions
EP2336701A3 (de
EP2336701B1 (de
Inventor
Debashis Ghosh
James A. Acre
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.)
Mahle International GmbH
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP2336701A2 publication Critical patent/EP2336701A2/de
Publication of EP2336701A3 publication Critical patent/EP2336701A3/de
Application granted granted Critical
Publication of EP2336701B1 publication Critical patent/EP2336701B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • a heat exchanger assembly and more specifically, a heat exchanger assembly including louvered air fins for transferring heat between a refrigerant and a stream of air.
  • a vast number of heat transfer applications e.g. residential HVAC, electronics, etc., operate under very low thermal heat transfer potential. In other words, the temperature difference between the refrigerant and the stream of air entering the heat exchanger is not great. Additionally, the size and power of the fan propelling the stream of air through a heat exchanger is often limited by a number of constraints, e.g. power usage, noise, space, etc. For example, in a laptop computer, the size of the fan must be minimized to fit within the space constraints of the casing, and the power of the fan must be minimized to avoid draining the battery or producing undesirable noise. In these applications, the performance of the air fins in transferring heat between the refrigerant and the stream of air is critical. Air fins generally include louvers to increase heat transfer, but those louvers also create an undesirable pressure drop in the stream of air.
  • Kim'385 includes first and second manifolds spaced from one another.
  • a plurality of tubes extend in spaced relationship with one another between the first and second manifolds for conveying the refrigerant between the first and second manifolds.
  • a plurality of fins are disposed between adjacent tubes for transferring heat between the tubes and the stream of air.
  • Each of the fins has a front edge and a back edge and presents a plurality of legs extending transversely between the adjacent tubes.
  • Each of the legs of the fins defines a plurality of front long louvers disposed between the front and back edges for conveying the stream of air through the legs of the air fins with each of the long louvers having a long louver height and a long louver length.
  • the invention is about a heat exchanger assembly for transferring heat between a refrigerant and a stream of air, comprising a first manifold, a second manifold spaced from said first manifold, a plurality of tubes extending in spaced relationship with one another between said first and second manifolds for conveying the refrigerant between said first and second manifolds, a plurality of fins disposed between adjacent ones of said tubes for transferring heat between the refrigerant in said tubes and the stream of air, each of said fins having a front edge and a back edge and including a plurality of legs extending transversely between said adjacent tubes, each of said legs of said fins defining a plurality of front long louvers disposed between said front and back edges for conveying the stream of air through said legs of said air fins with each of said long louvers having a long louver height and a long louver length; and each of said legs of said fins defining a plurality of main spoilers disposed between said front long louvers and said
  • Each of said front spoilers extends outwardly from said legs and has a triangular shape and, each of said legs of said air fins defines a plurality of back spoilers disposed adjacent to said back edge and a plurality of back long louvers disposed between said micro-louvers and said back spoilers. Also, each of said legs of said fins has a fin height and said long louver height is in the range of 50 to 90 percent of said fin height.
  • the long louver length is in the range of 0.7 to 1.5 mm.
  • the spoiler length is in the range of 0.15 to 0.4 mm.
  • Each of said front long louvers extends diagonally outwardly from said legs of said fins.
  • the first and second manifolds extend in spaced and parallel relationship with one another.
  • the first manifold defines a plurality of first tube slots spaced from one another and said second manifold defines a plurality of second tube slots spaced from one another and aligned with said first tube slots.
  • Each of said tubes has a cross-section presenting flat sides interconnected by a round front and a round back.
  • the tubes extend in spaced and parallel relationship with one another between said aligned first and second tube slots of said first and second manifolds.
  • Each of said tubes defines a fluid passage for conveying the refrigerant between said manifolds.
  • the main spoilers are disposed in a staggered arrangement.
  • the main spoilers are semi-cylindrical bumps or triangular notches.
  • the invention provides for such a heat exchanger assembly and wherein each of the legs of the fins defines a plurality of main spoilers disposed between the front long louvers and the back edges for inducing turbulence in the stream of air with each of the main spoilers having a spoiler height in the range of 50 to 90 percent of the long louver height and each of the main spoilers having a spoiler length in the range of 10 to 35 percent of the long louver length.
  • the potential for heat transfer between the refrigerant and the stream of air decreases as the air flows downstream through the heat exchanger because the temperature difference between the refrigerant and the stream of air is reduced.
  • the long louvers have more potential for heat transfer than the main spoilers because the long louvers turn and induce turbulence to the stream of air, whereas the main spoilers function mainly to induce turbulence in the air. Therefore, the long louvers are disposed upstream, where the temperature difference between the stream of air and the refrigerant is greatest, of the main spoilers.
  • the upstream long louvers perform the majority of the heat transfer between the stream of air and the refrigerant.
  • long louvers create a large pressure drop in the stream of air flowing through the heat exchanger. Therefore, it is undesirable to have long louvers extend the entire length of the air fin.
  • the smaller main spoilers are disposed downstream of the long louvers to induce turbulence in the stream of air to increase the air's heat transfer potential without compromising the overall pressure drop of the heat exchanger. This allows for a greater quantity of air to flow through the upstream long louvers of the fins and improves the overall efficiency of the heat exchanger assembly.
  • Figure 1 is a perspective view of a heat exchanger assembly
  • Figure 2 is a perspective view, partially cut away a first embodiment of a fin with louvers and one tube of a heat exchanger assembly
  • Figure 3 is a front view, partially cut away of a first embodiment of a fin
  • Figures 4 a through f are cross-sectional views of the first through sixth embodiments of the louvers and spoilers of the fins;
  • Figure 5 is a cross-sectional view showing the flow of air over the louvers and spoilers according to one of the embodiment of Figure 4a ;
  • Figure 6 is a front view, partially cut away for an alternate embodiment of a fin having micro-louvers disposed in a staggered arrangement.
  • a heat exchanger assembly 20 for transferring heat between a refrigerant and a stream of air 22 is generally shown in Figure 1 .
  • the heat exchanger assembly 20 includes a first manifold 24 and a second manifold 26 extending in spaced and parallel relationship with one another.
  • the first manifold 24 defines a plurality of first tube slots 28 being spaced from one another.
  • the second manifold 26 defines a plurality of second tube slots 30 being spaced from each other and aligned with the first tube slots 28.
  • a plurality of tubes 32 extend in spaced and parallel relationship to one another between the aligned first and second tube slots 28, 30.
  • Each of the tubes 32 has a cross-section defining flat sides 34 interconnected by a round front 36 and a round back 38.
  • Each of the tubes 32 defines a fluid passage 40 for conveying refrigerant between the manifolds 24, 26.
  • a plurality of fins 42 are disposed between adjacent ones of the tubes 32 for transferring heat between the refrigerant in the fluid passages 40 of the tubes 32 and the stream of air 22.
  • the fins 42 have a fin height HF.
  • the fins 42 extend continuously between a front edge 44 adjacent to the round front 36 of the tubes 32 and back edge 46 adjacent to the round back 38 of the tubes 32. In other words, the front edge 44 of the fins 42 is upstream of the back edge 46 of the fins 42.
  • Each of the fins 42 includes a plurality of legs 48 extending transversely between the adjacent tubes 32.
  • the fins 42 also include a plurality of end portions 50 engaging the flat sides 34 of the adjacent tubes 32.
  • legs 48 and end portions 50 of the fins 42 present a serpentine path extending between the first and second manifolds 24, 26.
  • adjacent legs 48 of the fins 42 are connected by end portions 50 engaging opposite ones of the flat sides 34 of the adjacent tubes 32.
  • each of the legs 48 of the fins 42 presents a plurality of front long louvers 52 disposed between the front and back edges 44, 46.
  • the front long louvers 52 function to turn the stream of air 22.
  • the front long louvers 52 convey the stream of air 22 through the legs 48 of the air fins 42. This keeps the stream of air 22 in the heat exchanger longer and gives the stream of air 22 more time to receive heat from or dispense heat to the refrigerant in the tubes 32, depending on the application of the heat exchanger assembly 20.
  • the long louvers 52, 54 have a long louver height HL, which is preferably in the range of 60 to 90 percent of the fin height HF, and the long louvers 52, 54 have a long louver length LL, which is preferably in the range of 0.7 to 1.5 mm.
  • each of the legs 48 of the fins 42 presents a plurality of main spoilers 56, 58, 60 disposed between the front long louvers 52 and the back edge 46, i.e. downstream of the front long louvers 52.
  • the main spoilers 56, 58, 60 serve to interrupt the airflow and induce turbulence in the stream of air 22, but do not substantially turn the air as the front long louvers 52 do.
  • some air might be conveyed cross-stream between the legs 48 of the fins 42 through the main spoilers 56, 58, 60, the majority of the air is flows straight through the heat exchanger assembly 20.
  • Each of the main spoilers 56, 58, 60 has a spoiler height HS preferably in the range of 50 to 90 percent of the long louver height HL, and each of the main spoilers 56, 58, 60 has a spoiler length LS preferably in the range of 10 to 35 percent of the long louver length LL.
  • a small spoiler length LS compared to the long louver length LL keeps the airflow blockage due to the main spoilers 56, 58, 60 small, thereby achieving good heat transfer with a low pressure drop penalty.
  • each of the legs 48 of the fins 42 is symmetrical.
  • all of the embodiments include back long louvers 54 disposed between the main spoilers 56, 58, 60 and the back edge 46 of the air fin 42.
  • some of the embodiments include back spoilers 62 disposed between the back long louvers 54 and the back edge 46 of the air fin 42.
  • the symmetry of the fins 42 is primarily for manufacturing purposes because symmetrical fins 42 can be made less expensively than non-symmetrical fins 42. It should be appreciated that the main spoilers 56, 58, 60 could extend from the front long louvers 52 to the back edge 46, or the air fin 42 could be flat between the main spoilers 56, 58, 60 and the back edge 46.
  • each of the legs 48 of the fins 42 presents a plurality of front spoilers 64 adjacent to the front edge 44 for interrupting the flow and inducing turbulence in the stream of air 22.
  • the delta-wing, or triangular, shaped front spoilers 64 are best shown in Figures 2 and 3 .
  • the delta wings are disposed over the entire fin height HF.
  • the width and height of the delta-wings is comparable to the spoiler length LS.
  • the front spoilers 64 are most useful when used in a cold environment. In cold environments, frost has a tendency of building up on the front edge 44 of the fins 42 when there is large heat transfer rate between the air and the refrigerant at that front edge 44.
  • the frost can block the stream of air 22 from flowing through the heat exchanger, which drastically reduces the efficiency of the heat exchanger.
  • the front spoilers 64 disposed upstream of the front long louvers 52 ensure that the maximum rate of heat transfer takes place slightly downstream of the front edge 44 of the fins 42 to prevent the frost from building up on the front edge 44 of the fins 42.
  • the efficiency of the heat exchanger assembly 20 might be reduced in some operating conditions, i.e. in warm environments, heat exchanger assemblies 20 having front spoilers 64 can be used in a wider variety of operating conditions.
  • the main spoilers 56, 58, 60 of the first embodiment are micro-louvers 56.
  • the second embodiment, shown in Figure 4b is similar to the first embodiment, but the delta-wing shaped front spoilers 64 of the first embodiment are replaced with front micro-louvers 64, shaped similarly to the main spoilers 56, 58, 60.
  • the front micro-louvers 64 function similar to the delta-wing shaped front spoilers 64 of the first embodiment in that they interrupt the airflow and induce turbulence in the air, but leave the majority of the heat transfer to the long louvers 52, 54 disposed between the micro-louvers 64 and the main spoilers 56, 58, 60, which are also shown as micro-louvers 56.
  • the third embodiment shown in Figure 4c , has front long louvers 52 disposed upstream of the main spoilers 56, 58, 60, shown as micro-louvers 56. Because the third embodiment does not have front spoilers 64, airflow is steered in the cross stream direction by the front and back long louvers 52, 54. Airflow is mostly straight in the mid section.
  • the fourth embodiment shown in Figure 4d , shows the main spoilers 56, 58, 60 as being micro-louvers 56.
  • the micro-louvers 56 of the fourth embodiment extend outwardly on both sides of the legs 48 of the fins 42.
  • the fifth embodiment shown in Figure 4e , shows the main spoilers 56, 58, 60 as being semi-cylindrical bumps 58.
  • the semi-cylindrical bumps 58 extend outwardly on both sides of the legs 48 of the fins 42.
  • the sixth embodiment shown in Figure 4f , shows the main spoilers 56, 58, 60 as being triangular notches 60.
  • the triangular notches 60 extend outwardly from the leg 48 on opposite sides of the leg 48.
  • main spoilers 56, 58, 60 may take any number of shapes, not just those shown in Figures 4 a-f .
  • the main spoilers 56, 58, 60 can be disposed both upstream or downstream of at least one front long louver 52. Additionally, each of the main spoilers 56, 58, 60 must have a spoiler height HS in the range of 50 to 90 percent of the long louver height HL, and each of the main spoilers 56, 58, 60 must have a spoiler length LS in the range of 10 to 35 percent of the long louver length LL.
  • Figure 5 shows the stream of air 22 flowing through the heat exchanger assembly 20 of the first embodiment.
  • the air flows straight between the legs 48 of the fins 42 past the micro-louvers or the delta-wing shaped front spoilers 64.
  • the stream of air 22 flows downstream between the legs 42, most of the air is turned by the front long louvers 52 between the legs 42.
  • the stream of air 22 then straightens out as it passes the main spoilers 56, 58, 60.
  • the back long louvers 54 which are optional as explained above, turn the stream of air 22 again between the legs 42.
  • the stream of air 22 once again straightens out when it passes the delta-wing shaped back spoilers 62.
  • each of the front spoilers 64, front long louvers 52, main spoilers 56, 58, 60, back long louvers 54, and back spoilers 62 induces turbulence into the stream of air 22.
  • the micro-louver segment can be disposed anywhere symmetrically or asymmetrically within the fins 42.
  • the micro-louvers 56 can alternately be disposed in a staggered arrangement.
  • the staggered arrangement can be easily manufactured and provide for a large number of micro-louvers 56 with a smaller pressure drop penalty.
  • the staggered micro-louvers 56 are disposed close to the end portions 50 of the fins 42, which have the a higher heat transfer potential than the middle of the fins 42.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP10193609.4A 2009-12-14 2010-12-03 Rippe mit niedrigem druckverlust mit selektiver mikrooberflächenverbesserung Not-in-force EP2336701B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US12/636,843 US20110139414A1 (en) 2009-12-14 2009-12-14 Low Pressure Drop Fin with Selective Micro Surface Enhancement

Publications (3)

Publication Number Publication Date
EP2336701A2 true EP2336701A2 (de) 2011-06-22
EP2336701A3 EP2336701A3 (de) 2017-05-31
EP2336701B1 EP2336701B1 (de) 2018-10-24

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EP10193609.4A Not-in-force EP2336701B1 (de) 2009-12-14 2010-12-03 Rippe mit niedrigem druckverlust mit selektiver mikrooberflächenverbesserung

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US (1) US20110139414A1 (de)
EP (1) EP2336701B1 (de)

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FR3013821A1 (fr) * 2013-11-25 2015-05-29 Valeo Systemes Thermiques Intercalaires pour echangeur thermique a persiennes decalees
CN106683832A (zh) * 2017-03-06 2017-05-17 常熟市友邦散热器有限责任公司 蜂窝形油道片式散热器
CN106816275A (zh) * 2017-03-06 2017-06-09 常熟市友邦散热器有限责任公司 带螺旋纽带的片式散热器
WO2018161419A1 (zh) * 2017-03-09 2018-09-13 南通江华热动力机械有限公司 一种轻质强冷却扰流元件
US10247481B2 (en) 2013-01-28 2019-04-02 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
FR3115099A1 (fr) * 2020-10-13 2022-04-15 Renault S.A.S. Echangeur de chaleur integre dans un moteur thermique a injection indirecte de carburant
EP4023993A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher
EP4023996A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher
EP4023995A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher
EP4023988A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher

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US9671176B2 (en) * 2012-05-18 2017-06-06 Modine Manufacturing Company Heat exchanger, and method for transferring heat
KR101977817B1 (ko) * 2013-02-01 2019-05-14 한온시스템 주식회사 열교환기
CN105051479B (zh) 2013-03-15 2017-05-31 达纳加拿大公司 具有嵌套凸片的传热表面
TWM512730U (zh) * 2015-08-20 2015-11-21 Cooler Master Co Ltd 水冷式散熱裝置
EP3362759B1 (de) * 2015-10-12 2022-07-27 Carrier Corporation Wärmetauscher für hlk-geräte im wohnbereich
CN205352165U (zh) * 2015-12-16 2016-06-29 杭州三花微通道换热器有限公司 换热器芯体和具有它的换热器
EP3330657B1 (de) * 2016-12-01 2020-10-28 Modine Manufacturing Company Luftrippe für einen wärmetauscher und verfahren zur herstellung davon
FR3106000B1 (fr) * 2020-01-03 2022-01-14 Valeo Systemes Thermiques Échangeur de chaleur à tubes comportant des intercalaires

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10247481B2 (en) 2013-01-28 2019-04-02 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
FR3013821A1 (fr) * 2013-11-25 2015-05-29 Valeo Systemes Thermiques Intercalaires pour echangeur thermique a persiennes decalees
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
CN106683832A (zh) * 2017-03-06 2017-05-17 常熟市友邦散热器有限责任公司 蜂窝形油道片式散热器
CN106816275A (zh) * 2017-03-06 2017-06-09 常熟市友邦散热器有限责任公司 带螺旋纽带的片式散热器
WO2018161419A1 (zh) * 2017-03-09 2018-09-13 南通江华热动力机械有限公司 一种轻质强冷却扰流元件
FR3115099A1 (fr) * 2020-10-13 2022-04-15 Renault S.A.S. Echangeur de chaleur integre dans un moteur thermique a injection indirecte de carburant
EP4023993A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher
EP4023996A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher
EP4023995A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher
EP4023988A1 (de) * 2020-12-29 2022-07-06 Valeo Autosystemy SP. Z.O.O. Wärmetauscher

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Publication number Publication date
US20110139414A1 (en) 2011-06-16
EP2336701A3 (de) 2017-05-31
EP2336701B1 (de) 2018-10-24

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