WO2013080892A1 - インナーフィン - Google Patents
インナーフィン Download PDFInfo
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- WO2013080892A1 WO2013080892A1 PCT/JP2012/080385 JP2012080385W WO2013080892A1 WO 2013080892 A1 WO2013080892 A1 WO 2013080892A1 JP 2012080385 W JP2012080385 W JP 2012080385W WO 2013080892 A1 WO2013080892 A1 WO 2013080892A1
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- WIPO (PCT)
- Prior art keywords
- protrusion
- inner fin
- tube
- exhaust gas
- gas flow
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
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- 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
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
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- 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 an inner fin that is mainly housed in an EGR cooler and is housed in a tube that allows exhaust gas to pass through, and promotes heat exchange of the exhaust gas.
- the plate material is pressed into a corrugated plate shape on a rectangular wave having unevenness in the width direction, and this repetition is performed in the gas flow direction.
- some inner fins used in EGR coolers have a heat exchange area that is expanded by making the unevenness in the width direction of the inner fins (hereinafter referred to as fin pitch) fine in order to improve the heat dissipation performance of the tube. (Patent Document 1).
- the present invention has been made to solve the above-mentioned problems, promotes heat exchange between exhaust gas and cooling water, is less likely to cause performance degradation due to clogging of soot, and is easy to assemble at the time of manufacture.
- An object of the present invention is to provide an inner fin for a tube of an EGR cooler.
- 1st invention is an inner fin used for the flat tube which is equipped with the EGR cooler which cools exhaust gas, and lets exhaust gas pass, Comprising: While forming a board
- the first protrusion “inclined to the upstream side in the gas flow direction” includes the case where the first protrusion is inclined at a size of less than 90 degrees to the left or right from the upstream direction.
- “Inclined downstream in the direction” includes the case where it is inclined at a size of less than 90 degrees to the left or right from the downstream direction.
- the second invention is characterized in that a distance Lc between the first protrusion and the second protrusion is not less than 0.5 times and not more than 1.5 times a height Lh of the first protrusion and the second protrusion.
- the third invention is characterized in that the first protrusion and the second protrusion are formed symmetrically with respect to the center position of the segment.
- the plate material is formed in a shape in which irregularities are repeated in the width direction, and this repetition is formed in an offset shape that is alternately shifted to the left and right for each predetermined length in the gas flow direction.
- the first protrusion By forming the second projection inclined to the downstream side in the gas flow direction at an angle equal to the inclination angle of the gas, the exhaust gas flowing into the segment is actively promoted to turbulent flow by the first projection, and the second projection Therefore, the heat dissipation performance of the tube can be improved without reducing the fin pitch.
- soot contained in the exhaust gas accumulates on the upstream side of the first protrusion inclined to the upstream side, and hardly accumulates on the second protrusion inclined to the downstream side. Therefore, it is possible to suppress the deterioration of the heat dissipation performance of the tube and prolong the product life.
- the distance Lc between the first protrusion and the second protrusion is not less than 0.5 times and not more than 1.5 times the height Lh of the first protrusion and the second protrusion.
- the first protrusion and the second protrusion are formed symmetrically with respect to the center position of the segment.
- FIG. 1 It is a perspective view which shows the EGR cooler using the inner fin which concerns on embodiment of this invention.
- A is a partial perspective view of the inner fin
- (b) is a partial plan view of the inner fin.
- (A) is side explanatory drawing which shows the inside of the segment of the inner fin
- (b) is explanatory drawing of the use condition of the inner fin.
- an EGR cooler in which the inner fin 1 is used has a large number of cylindrical shells 2 formed by combining a pair of U-shaped members made of SUS (stainless steel).
- a flat SUS tube 3 is laminated at a predetermined interval to form a core portion 4.
- a SUS inlet header 5 for supplying exhaust gas to the tube 3 and a SUS outlet header 6 for discharging the exhaust gas from the tube 3 are attached to both ends of the core portion 4 where the tube 3 is open. ing.
- a cooling water inlet pipe 7 that supplies cooling water is connected to the lower surface portion of the inlet side of the shell 2, and a cooling water outlet pipe 8 that leads out the cooling water is connected to the upper surface portion of the outlet side of the shell 2.
- the exhaust gas branches and passes through a number of tubes 3, and the cooling water flows through the cooling water flow path between the tubes 3 and the shell 2. Cooled by exchange.
- the tube 3 includes a tube inner in which inner side walls are erected on both side ends of a substantially flat flat plate portion, and a tube outer in which outer side walls that circumscribe the inner side wall are erected on both side ends of the substantially flat flat plate portion.
- a tube inner in which inner side walls are erected on both side ends of a substantially flat flat plate portion
- a tube outer in which outer side walls that circumscribe the inner side wall are erected on both side ends of the substantially flat flat plate portion.
- the tube inner and the tube outer are joined by brazing.
- the bulging part which bulged the flat plate part in the thickness direction is formed in the longitudinal direction both ends of the tube inner and the tube outer. For this reason, when a large number of tubes 3 are stacked, the bulging portion comes into contact with another tube 3, thereby providing a predetermined gap serving as a cooling water flow path between the tubes 3.
- Each tube 3 accommodates the offset-shaped inner fin 1 to promote the turbulent flow of the exhaust gas passing through the inside, increase the heat exchange area between the exhaust gas and the cooling water, and promote the heat exchange. is doing.
- the inner fin 1 is disposed between the tube inner and the tube outer when they are assembled, and is brazed to the flat portion of the tube inner and the tube outer at the upper surface portion and the lower surface portion.
- the inner fin 1 repeats irregularities in the width direction (left and right direction) of the SUS plate material and alternately repeats this for every predetermined length in the gas flow direction (front and rear direction). It is formed in an offset shape shifted left and right.
- the left / right shift amount is set to about one-fourth of the fin pitch Fp (half of the concave or convex in the width direction).
- the inner fin is provided with a large number of segments 10 surrounded by a pair of left and right side walls in the longitudinal direction and the width direction.
- the inner fin 1 has a first protrusion 11 that cuts and raises a part of the upper surface portion or the lower surface portion for each segment 10 and protrudes into the gas passage.
- the second protrusion 12 is formed.
- the first protrusion 11 and the second protrusion 12 are both cut and raised in a trapezoidal shape, and the first protrusion 11 disposed on the upstream side in the gas flow direction is inclined upstream, and the second protrusion is disposed on the downstream side in the gas flow direction. 12 is inclined in the opposite direction of the first protrusion, that is, downstream.
- Fig.3 (a) since the 1st protrusion 11 and the 2nd protrusion 12 are cut and raised by the angle of the same magnitude
- the first protrusion 11 formed on the lower surface portion of the specific segment 10a is inclined to the upstream left side and the second protrusion 12 is inclined to the downstream right side
- the first protrusion 11 is adjacent to the right and left sides.
- the first protrusion 11 formed on the upper surface portion is inclined to the upstream left side at the same angle
- the second protrusion 12 is inclined to the downstream right side at the same angle.
- the first protrusion 11 is inclined to the upstream right side
- the second protrusion 12 is inclined to the downstream left side.
- the first protrusion 11 of the specific segment 10a is inclined to the left with respect to the gas flow direction, and the first protrusions 11 of the segments 10c and 10d adjacent to the upstream side or the downstream side thereof are in the gas flow direction.
- the angle at which the second protrusion 12 of the specific segment 10a is inclined to the right with respect to the gas flow direction and the segment adjacent to the upstream side or the downstream side are equal to each other.
- the size of the angle at which the second protrusions 12 of 10c and 10d are inclined leftward with respect to the gas flow direction is also equal.
- the right and left tilt angles of the first protrusion 11 and the second protrusion 12 and the angle of raising and lowering in the height direction are optimal according to the ventilation resistance of the EGR cooler used and the flow rate of exhaust gas per unit time. Adjust so that
- the broken-line arrows in FIGS. 3A and 3B indicate the flow of exhaust gas.
- the first protrusion 11 is inclined to the upstream side in the gas flow direction, and has a shape that positively causes turbulence in the exhaust gas flowing into the segment 10. Since the second protrusion 12 is inclined to the downstream side in the gas flow direction, the exhaust gas whose turbulence is promoted by the first protrusion 11 is diffused to the two left and right segments 10 so as to flow smoothly. It has become.
- the distance Lc between the first protrusion 11 and the second protrusion 12 is 0.5 times or more and 1.5 times the height Lh of the first protrusion 11 and the second protrusion 12. It is preferable to set as follows. When Lc is larger than 1.5 times Lh, the first projection 11 and the second projection 12 do not function synergistically, and the exhaust gas whose turbulence is promoted by the first projection 11 is caused by the second projection 12. The effect of smooth diffusion cannot be obtained. Further, if Lc is smaller than 0.5 times Lh, when the first protrusion 11 and the second protrusion 12 are formed on the inner fin 1, there is a possibility that the molding cannot be performed due to the influence of the mold strength. The heat dissipation performance of the tube 3 can be improved as Lc is set smaller within the range of 0.5 to 1.5 times Lh.
- the center of the first protrusion 11 and the second protrusion 12 coincides with the center of the segment 10, and the first protrusion 11 and the second protrusion 12 are the center of the segment 10.
- the exhaust gas dispersed and flowing into each segment 10 is turbulent by the first protrusion 11 inclined to the upstream side, and then the second inclined to the downstream side. Since the projection 12 smoothly diffuses to the downstream segment 10, heat exchange between the exhaust gas and the cooling water is promoted, and the heat dissipation performance of the tube 3 can be improved.
- the distance Lc between the first protrusion 11 and the second protrusion 12 is set to 0.5 times or more and 1.5 times or less the height Lh of the first protrusion 11 and the second protrusion 12, the first protrusion 11 It is possible to achieve both improvement in heat dissipation performance due to the synergistic action of the first protrusion 11 and the second protrusion 12 and ease of forming the inner fin 1.
- first protrusion 11 and the second protrusion 12 are formed symmetrically with respect to the center of the segment 10, and even if the first protrusion 11 and the second protrusion 12 are rotated 180 degrees in the horizontal direction, the internal structure of the segment 10 with respect to the exhaust gas flow does not change. Therefore, even if the inner fins 1 are arranged upside down when the tube 3 is assembled, the heat dissipation performance of the tube 3 does not deteriorate, there is no risk of erroneous assembly during manufacture, and the quality of the tube 3 is improved. It can be stabilized.
- a tube containing an inner fin (Example) according to an embodiment of the present invention a tube containing an inner fin (Comparative Example 1) provided with neither a first protrusion nor a second protrusion as shown in FIG.
- a fluid analysis is performed when exhaust gas is flowed at a flow rate of 15 m / s, and the heat dissipation performance is compared. The result was as shown in FIG.
- Inner fin 1: Inner fin, 2: Shell, 3: Tube, 4: Core part, 5: Inlet header, 6: Outlet header, 7: Cooling water inlet pipe, 8: Cooling water outlet pipe, 9: (Conventional) inner fin 10 (10a, 10b, 10c, 10d): segment, 11: first protrusion, 12: second protrusion, 13: ridge
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
Description
また、EGRクーラに用いられるインナーフィンには、チューブの放熱性能を向上させるために、インナーフィンの幅方向の凹凸(以下、フィンピッチという)を細かくすることで熱交換面積を拡大したものがあった(特許文献1)。
また、チューブの断面積においてインナーフィンの占める割合が大きくなるため、排気ガスに含まれる煤、PM(パティキュレートマター)等が堆積しやすくなり、チューブに詰まりが発生し、熱交換器としての機能を失ってしまうおそれがあった。
さらに、フィンピッチを細かくすると、インナーフィンの展開長が長くなり、材料が増えるため、材料コストが増加してしまった。
また、特許文献2の構成では、このような突起はガス流れ方向(前後方向)に方向性を持つ形状に形成されたものが多く、製造時にインナーフィンをチューブに対して前後逆に組み付けてしまうと、所定の性能を発揮することができなかった。
また、一つ一つの突起が乱流促進のために直立しているため、長期の使用に伴って排気ガスに含まれる煤やPMが突起に堆積しやすく、乱流促進機能の低下や熱伝達率の低下が生じるおそれがあった。
第1の発明は、排気ガスを冷却するEGRクーラに内装され、排気ガスを通過させる扁平なチューブに用いられるインナーフィンであって、板材を、幅方向に凹凸を繰り返す形状に形成するとともにこの繰り返しをガス流れ方向の所定長さごとに交互に左右にずらしたオフセット形状に形成し、一対の左右側壁で囲まれたセグメントごとに、上面部または下面部のいずれか一方を切り起こして、ガス流れ方向上流側に傾斜させた第一突起と、この第一突起の下流側に配置され、第一突起の傾斜角と等しい角度でガス流れ方向下流側に傾斜させた第二突起とを形成したことを特徴とする。
なお、第一突起が「ガス流れ方向上流側に傾斜している」とは、上流方向から左右のいずれかに90度未満の大きさで傾いている場合を含み、第二突起が「ガス流れ方向下流側に傾斜している」とは、下流方向から左右のいずれかに90度未満の大きさで傾いている場合を含むものとする。
また、EGRクーラの使用に伴って、排気ガスに含まれる煤が、上流側に傾斜した第一突起の上流側に溜まっても、下流側に傾斜した第二突起にはほとんど堆積しない。そのため、チューブの放熱性能の低下を抑え、製品寿命を長期化することができる。
このインナーフィン1が用いられるEGRクーラは、図1に示すように、一対の断面U字状のSUS(ステンレス鋼)製の部材を組み合わせてなる大径筒状のシェル2の内部に、多数の扁平なSUS製のチューブ3を所定の間隔を設けて積層し、コア部4を形成している。
また、シェル2の入口側下面部には冷却水を供給する冷却水入ロパイプ7が接続され、シェル2の出口側上面部には冷却水を導出する冷却水出ロパイプ8が接続されている。
このEGRクーラのコア部4では、排気ガスが多数のチューブ3に分岐して通過するとともに、冷却水がチューブ3とシェル2との間の冷却水流路を流れて、排気ガスが冷却水と熱交換によって冷却される。
このチューブ3では、チューブインナーおよびチューブアウターの長手方向両端において、平板部を厚さ方向に膨出させた膨出部を形成している。このため、多数のチューブ3を積層すると、この膨出部が他のチューブ3に当接することによって、チューブ3相互の間に冷却水流路となる所定の間隙が設けられる。
インナーフィン1は、チューブインナーおよびチューブアウターを組み立てる際に両者の問に配置され、上面部および下面部でチューブインナーおよびチューブアウターの平板部にろう付けされる。
これにより、インナーフィンには、一対の左右側壁で囲まれるセグメント10が長手方向および幅方向に多数設けられる。
第一突起11および第二突起12はともに台形状に切り起こされ、ガス流れ方向上流側に配置される第一突起11は上流側へ傾斜し、ガス流れ方向下流側に配置される第二突起12は第一突起の反対方向、すなわち下流側へ傾斜している。図3(a)に示すように、第一突起11と第二突起12とは、反対方向に同じ大きさの角度で切り起こしているため、図3(a)上で(側面視で)、第一突起11が左上方に突出し、第突起12が右上方に突出している。
また、図2(b)に示すように、第一突起11は、ガス流れ方向(前後方向)に対して左右のいずれかに傾斜しており、その下流側の第二突起12は、この第一突起11と左右の反対方向に同じ角度で傾斜している。
他方、上記特定のセグメント10aの上流側または下流側に隣接するセグメント10c、10dでは、第一突起11が上流右側へ傾斜し、第二突起12が下流左側へ傾斜している。なお、上記特定のセグメント10aの第一突起11がガス流れ方向に対して左側へ傾斜する角度の大きさと、その上流側または下流側に隣接するセグメント10c、10dの第一突起11がガス流れ方向に対して右側へ傾斜する角度の大きさは等しく、上記特定のセグメント10aの第二突起12がガス流れ方向に対して右側へ傾斜する角度の大きさと、その上流側または下流側に隣接するセグメント10c、10dの第二突起12がガス流れ方向に対して左側へ傾斜する角度の大きさも等しい。
第一突起11および第二突起12の左右への傾きの角度および高さ方向の切り起こしの角度は、使用されるEGRクーラの通気抵抗や排気ガスの単位時間あたりの流量に応じて、最適となるように調整する。
第一突起11は、ガス流れ方向上流側に傾斜しており、セグメント10に流入する排気ガスに積極的に乱流を起こす形状になっている。
第二突起12は、ガス流れ方向下流側に傾斜しているため、第一突起11で乱流化を促進された排気ガスを下流側の左右2つのセグメント10へ拡散して円滑に流すようになっている。
LcをLhの1.5倍より大きくすると、第一突起11と第二突起12とが相乗的に機能せず、第一突起11で乱流化を促進された排気ガスを第二突起12で円滑に拡散するという効果が得られなくなってしまう。
また、LcをLhの0.5倍よりも小さくすると、インナーフィン1に第一突起11および第二突起12を形成する際に、金型強度の影響により成形できなくなるおそれがある。Lhの0.5~1.5倍の範囲内でLcを小さく設定するほどチューブ3の放熱性能を向上させることができる。
本発明の実施形態に係るインナーフィン(実施例)を収容したチューブと、図5のように第一突起も第二突起も設けないインナーフィン(比較例1)を収容したチューブと、各セグメントに第一突起のみを設けて第二突起を設けないインナーフィン(比較例2)を収容したチューブとについて、排気ガスを流速15m/sで流した場合の流体解析を行い、放熱性能を比較したところ、図4のような結果となった。
したがって、第一突起11および第二突起12を設けた実施例では、第一突起および第二突起を設けない比較例1に対し放熱性能が21.9%向上し、第一突起のみを設けた比較例2に対しても、放熱性能が約3.8%向上することがわかった。
本出願は、2011年11月30日出願の日本特許出願・出願番号2011-261325に基づくものであり、その内容はここに参照として取り込まれる。
Claims (3)
- 排気ガスを冷却するEGRクーラに内装され、排気ガスを通過させる扁平なチューブに用いられるインナーフィンであって、
板材を、幅方向に凹凸を繰り返す形状に形成するとともにこの繰り返しをガス流れ方向の所定長さごとに交互に左右にずらしたオフセット形状に形成し、
一対の左右側壁で囲まれたセグメントごとに、上面部または下面部のいずれか一方を切り起こして、ガス流れ方向上流側に傾斜させた第一突起と、この第一突起の下流側に配置され、第一突起の傾斜角と等しい角度でガス流れ方向下流側に傾斜させた第二突起とを形成したことを特徴とするインナーフィン。 - 上記第一突起と上記第二突起との距離Lcが、上記第一突起および上記第二突起の高さLhの0.5倍以上1.5倍以下であることを特徴とする請求項1に記載のインナーフィン。
- 上記セグメントの中心位置に対し、上記第一突起と上記第二突起とが対称に形成されていることを特徴とする請求項1に記載のインナーフィン。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MX2014006544A MX355946B (es) | 2011-11-30 | 2012-11-22 | Aleta interna. |
US14/361,914 US20140345578A1 (en) | 2011-11-30 | 2012-11-22 | Inner Fin |
EP12854375.8A EP2787315B1 (en) | 2011-11-30 | 2012-11-22 | Inner fin |
CN201280058935.4A CN103975217A (zh) | 2011-11-30 | 2012-11-22 | 内散热片 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2011-261325 | 2011-11-30 | ||
JP2011261325A JP5887115B2 (ja) | 2011-11-30 | 2011-11-30 | インナーフィン |
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WO2013080892A1 true WO2013080892A1 (ja) | 2013-06-06 |
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US (1) | US20140345578A1 (ja) |
EP (1) | EP2787315B1 (ja) |
JP (1) | JP5887115B2 (ja) |
CN (2) | CN103975217A (ja) |
MX (1) | MX355946B (ja) |
WO (1) | WO2013080892A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014175158A1 (ja) * | 2013-04-23 | 2014-10-30 | カルソニックカンセイ株式会社 | 熱交換器 |
WO2014188942A1 (ja) * | 2013-05-23 | 2014-11-27 | カルソニックカンセイ株式会社 | 熱交換器 |
WO2014198846A1 (de) * | 2013-06-14 | 2014-12-18 | Behr Gmbh & Co. Kg | Wärmeübertrager |
JP2016099046A (ja) * | 2014-11-20 | 2016-05-30 | カルソニックカンセイ株式会社 | 熱交換器 |
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JP5915187B2 (ja) * | 2012-01-10 | 2016-05-11 | マツダ株式会社 | 熱交換器 |
JP2015132420A (ja) * | 2014-01-14 | 2015-07-23 | 株式会社ミクニ | 熱交換器用伝熱管および熱交換器 |
JP2016080325A (ja) * | 2014-10-22 | 2016-05-16 | カルソニックカンセイ株式会社 | 熱交換器 |
JP6347719B2 (ja) * | 2014-10-22 | 2018-06-27 | カルソニックカンセイ株式会社 | 熱交換器 |
JP2016080323A (ja) * | 2014-10-22 | 2016-05-16 | カルソニックカンセイ株式会社 | 熱交換器 |
FR3030707B1 (fr) * | 2014-12-18 | 2019-04-05 | Valeo Systemes Thermiques | Ensemble de transfert de chaleur pour un echangeur de chaleur |
CN106246417A (zh) * | 2016-09-30 | 2016-12-21 | 无锡金轮达科技有限公司 | 一种新型锯齿形egr冷却器散热翅片 |
JP6550177B1 (ja) * | 2018-07-20 | 2019-07-24 | カルソニックカンセイ株式会社 | 熱交換器 |
CN111426228B (zh) * | 2020-05-18 | 2021-06-15 | 安徽东能换热装备有限公司 | 一种板式换器的格栅式扰流装置 |
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- 2012-11-22 WO PCT/JP2012/080385 patent/WO2013080892A1/ja active Application Filing
- 2012-11-22 US US14/361,914 patent/US20140345578A1/en not_active Abandoned
- 2012-11-22 MX MX2014006544A patent/MX355946B/es active IP Right Grant
- 2012-11-22 CN CN201811242938.9A patent/CN109631650A/zh active Pending
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2014175158A1 (ja) * | 2013-04-23 | 2014-10-30 | カルソニックカンセイ株式会社 | 熱交換器 |
US10386132B2 (en) | 2013-04-23 | 2019-08-20 | Calsonic Kansei Corporation | Heat exchanger |
WO2014188942A1 (ja) * | 2013-05-23 | 2014-11-27 | カルソニックカンセイ株式会社 | 熱交換器 |
JP2014228208A (ja) * | 2013-05-23 | 2014-12-08 | カルソニックカンセイ株式会社 | 熱交換器 |
US10197336B2 (en) | 2013-05-23 | 2019-02-05 | Calsonic Kansei Corporation | Heat exchanger |
WO2014198846A1 (de) * | 2013-06-14 | 2014-12-18 | Behr Gmbh & Co. Kg | Wärmeübertrager |
JP2016099046A (ja) * | 2014-11-20 | 2016-05-30 | カルソニックカンセイ株式会社 | 熱交換器 |
Also Published As
Publication number | Publication date |
---|---|
EP2787315B1 (en) | 2017-01-11 |
US20140345578A1 (en) | 2014-11-27 |
CN103975217A (zh) | 2014-08-06 |
MX2014006544A (es) | 2014-10-24 |
JP5887115B2 (ja) | 2016-03-16 |
JP2013113523A (ja) | 2013-06-10 |
EP2787315A1 (en) | 2014-10-08 |
CN109631650A (zh) | 2019-04-16 |
EP2787315A4 (en) | 2015-12-30 |
MX355946B (es) | 2018-05-07 |
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