US20080011464A1 - Exhaust gas heat exchanger - Google Patents

Exhaust gas heat exchanger Download PDF

Info

Publication number
US20080011464A1
US20080011464A1 US11/827,409 US82740907A US2008011464A1 US 20080011464 A1 US20080011464 A1 US 20080011464A1 US 82740907 A US82740907 A US 82740907A US 2008011464 A1 US2008011464 A1 US 2008011464A1
Authority
US
United States
Prior art keywords
exhaust gas
fin
inner fin
tube
heat exchanger
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.)
Abandoned
Application number
US11/827,409
Other languages
English (en)
Inventor
Yuu Oofune
Takayuki Hayashi
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.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAYASHI, TAKAYUKI, OOFUNE, YUU
Publication of US20080011464A1 publication Critical patent/US20080011464A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • 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
    • 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
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • F02M26/38—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with two or more EGR valves disposed in parallel
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to an exhaust gas heat exchanger.
  • the exhaust gas heat exchanger can be suitably used for an exhaust gas recirculation cooler (EGR cooler), which is provided in an exhaust gas recirculation device (EGR) to cool exhaust gas.
  • EGR cooler exhaust gas recirculation cooler
  • EGR exhaust gas recirculation device
  • an exhaust gas recirculation cooler (EGR cooler) is used in a diesel type engine or the like as an exhaust gas heat exchanger.
  • EGR cooler exhaust gas recirculation cooler
  • the general EGR cooler is arranged at a halfway position of an exhaust gas recirculation pipe for partially refluxing exhaust gas of the engine directly to the suction side of the engine.
  • the EGR cooler is provided with multiple tubes which are stacked and in each of which an inner fin is arranged. Exhaust gas flowing in the tube is heat-exchanged with cooling water flowing at the outer side of the tube, so that exhaust gas is cooled.
  • the inner fin is constructed of a straight fin.
  • the inner fin can be also constructed of an offset fin which is generally used in an inter cooler or the like to have a different use from the EGR cooler, for example, with reference to JP-3766914.
  • the offset fin is susceptible to being clogged, although having a higher heat-exchanging capacity than the straight fin. Because there is lot of coal in exhaust gas flowing through the EGR cooler so that the offset fin is susceptible to be clogged, it is difficult to use the offset fin as the inner fin of the EGR cooler.
  • the cooling method, the required performance, the specifications environment and the like of the EGR cooler are different from those of the inter cooler, specifications (such as fin pitch fp, fin height fh, segment length L and the like) of the offset fin used in the inter cooler can not be directly (without being changed) used in the EGR cooler.
  • the cooling method of the inter cooler is different from that of the EGR cooler. That is, the inter cooler is generally an air cooling type, while the EGR cooler is generally a water cooling type. Thus, the contribution degree of the inner fin to the heat exchanging capacity in the inter cooler is different from that in the EGR cooler.
  • the temperature (e.g., 170° C.) of the cooling object gas of the inter cooler is different from that (e.g., 400° C.) of the EGR cooler.
  • the inter cooler is made of a different material from that of the EGR cooler.
  • the inter cooler is generally made of aluminum.
  • the EGR cooler is to be made of a stainless steel to maintain a corrosion resistance, because the EGR cooler is exposed to a corrosion environment due to high-temperature oxidation and condensation water.
  • the specifications of the offset fin are set in such a manner that the heat exchanging capacity (related to cooling method, temperature of cooling object gas, material of inner fin and the like) of the EGR cooler has a maximum value.
  • the heat exchanging capacity of the EGR cooler will be lowered.
  • an object of the present invention to provide an exhaust gas heat exchanger having an improved performance in the case where an offset fin is used as an inner fin.
  • an exhaust gas heat exchanger in which exhaust gas generated due to combustion is heat-exchanged with cooling fluid includes a tube in which the exhaust gas flows and outside which the cooling fluid flows, and an inner fin which is arranged in the tube to improve a heat exchange between the exhaust gas and the cooling fluid.
  • the inner fin has a cross section which has a corrugated shape to include convex portions positioned at crests and troughs of the corrugated shape, and is constructed of an offset fin having lanced segments which are partially lanced and arrayed substantially in a flowing direction of the exhaust gas.
  • the crests and the troughs are alternately arranged, and the cross section is substantially perpendicularly to the flowing direction of the exhaust gas.
  • a fin pitch fp and a fin height fh of the inner fin (32) are defined by 3.5 mm ⁇ fh ⁇ 12 mm, and 2 mm ⁇ fp ⁇ 12 mm, wherein the fin pitch fp is a distance between central lines of the adjacent convex portions positioned at a side of one of the crest and the trough in the cross section of the inner fin, and the fin height fh is a distance between the convex portions which are respectively positioned at the side of the crest and the side of the trough in the cross section of the inner fin.
  • the pressure loss of the exhaust gas flowing in the tube and the hydraulic resistance of the cooling fluid can be restricted. Therefore, the tube can be restricted from being clogged, and can be provided with a higher heat-radiating capacity.
  • an exhaust gas heat exchanger in which exhaust gas generated due to combustion is heat-exchanged with cooling fluid is provided with a tube in which the exhaust gas flows and outside which the cooling fluid flows, and an inner fin which is arranged in the tube to improve a heat exchange between the exhaust gas and the cooling fluid.
  • the inner fin has a cross section which has a corrugated shape to include convex portions positioned at crests and troughs of the corrugated shape, and is constructed of an offset fin having lanced segments which are partially lanced and arrayed substantially in a flowing direction of the exhaust gas.
  • the crests and the troughs are alternately arranged, and the cross section is substantially perpendicularly to the flowing direction of the exhaust gas.
  • An equivalent circle diameter de is defined by following formulas
  • L is a length of the lanced segment in the flowing direction of the exhaust gas
  • the equivalent circle diameter de is a diameter of an equivalent circle of a field C which is surrounded by the inner fin and the tube and positioned between the adjacent convex portions at a side of one of the crest and the trough of the corrugated shape in the cross section of the inner fin.
  • the gas density which is a factor considering both the cooling capacity and the pressure loss will be larger than or equal to 93%, so that the exhaust gas heat exchanger has an improved performance can be provided.
  • an exhaust gas heat exchanger in which exhaust gas generated due to combustion is heat-exchanged with cooling fluid is provided with a tube in which the exhaust gas flows and outside which the cooling fluid flows, and an inner fin which is arranged in the tube to improve a heat exchange between the exhaust gas and the cooling fluid.
  • the inner fin has a cross section which has a corrugated shape to include convex portions positioned at crests and troughs of the corrugated shape, and is constructed of an offset fin having lanced segments which are partially lanced and arrayed substantially in a flowing direction of the exhaust gas. The crests and the troughs are alternately arranged, and the cross section is substantially perpendicularly to the flowing direction of the exhaust gas.
  • a length L of the lanced segment is defined by following formulas
  • the length L is a dimension in the flowing direction of the exhaust gas
  • fp is a fin pitch which is a distance between central lines of the adjacent convex portions positioned at a side of one of the crest and the trough in the cross section of the inner fin
  • fh is a fin height which is a distance between the convex portions which are respectively positioned at the side of the crest and the side of the trough in the cross section of the inner fin.
  • the gas density can be larger than or equal to 97%.
  • the exhaust gas heat exchanger has the further improved performance can be provided.
  • an exhaust gas heat exchanger in which exhaust gas generated due to combustion is heat-exchanged with cooling fluid is provided with a tube in which the exhaust gas flows and outside which the cooling fluid flows, and an inner fin which is arranged in the tube to improve a heat exchange between the exhaust gas and the cooling fluid.
  • the inner fin has a cross section which has a corrugated shape to include convex portions positioned at crests and troughs of the corrugated shape, and is constructed of an offset fin having lanced segments which are partially lanced and arrayed substantially in a flowing direction of the exhaust gas. The crests and the troughs are alternately arranged, and the cross section is substantially perpendicularly to the flowing direction of the exhaust gas.
  • a fin pitch fp and a length L of the lanced segment are substantially defined by following formulas
  • the length L is a dimension in the flowing direction of the exhaust gas
  • fh is a fin height which is a distance between the convex portions respectively positioned at a side of the crest and a side of the trough in the cross section of the inner fin
  • de is an equivalent circle diameter which is a diameter of an equivalent circle of a field C surrounded by the inner fin and the tube and positioned between the adjacent convex portions of the side of one of the crest and the trough in the cross section of the inner fin
  • the fin pitch fp is a distance between central lines of the adjacent convex portions positioned at a side of one of the crest and the trough in the cross section of the inner fin.
  • the gas density can be larger than or equal to 93%, so that the exhaust gas heat exchanger has an improved performance can be provided.
  • FIG. 1 is a schematic view showing an exhaust gas recirculation device where an exhaust gas heat exchanger is used according to a first embodiment of the present disclosure
  • FIG. 2 is a schematic side view showing an EGR cooler as the exhaust gas heat exchanger according to the first embodiment
  • FIG. 3 is a schematic sectional view taken along the line III-III in FIG. 2 ;
  • FIG. 4 is a schematic sectional view taken along the line IV-IV in FIG. 3 ;
  • FIG. 5 is a schematic perspective view showing the EGR cooler according to the first embodiment
  • FIG. 6 is a schematic sectional view of an inner fin of the EGR cooler which is taken along a direction substantially perpendicular to an exhaust gas flowing direction according to the first embodiment
  • FIG. 7 is a graph showing a relation between a fin height of an offset fin and a pressure loss ratio according to the first embodiment
  • FIG. 8 is a graph showing a relation between the fin height and a hydraulic resistance according to the first embodiment
  • FIG. 9 is a schematic sectional view showing an inner fin of an EGR cooler which is taken along a direction substantially perpendicular to an exhaust gas flowing direction according to a second embodiment of the present disclosure
  • FIG. 10 is a graph showing a relation between an equivalent circle diameter of an offset fin and an EGR gas density ratio according to the second embodiment
  • FIG. 11 is a graph showing a relation between a segment length of an offset fin and an EGR gas density ratio according to a third embodiment of the present disclosure.
  • FIG. 12 is a graph showing a relation between an EGR gas density ratio and a function using an equivalent circle diameter, a segment length and a fin height according to a fourth embodiment of the present disclosure
  • FIG. 13A is a graph showing a variation of a PM advantage sedimentation thickness at the offset fin with respect to time
  • FIG. 13B is a schematic view showing a sedimentation of PM at the offset fin
  • FIG. 14 is a graph showing a relation between a heat radiating performance of the EGR cooler and a fin pitch of the offset fin.
  • the exhaust gas heat exchanger can be suitably used as an exhaust gas recirculation cooler 10 (EGR cooler), for example.
  • EGR cooler exhaust gas recirculation cooler
  • the EGR cooler 10 can be provided for an exhaust gas recirculation device.
  • the exhaust gas recirculation device has, for example, an air cleaner 3 , a variable tube actuator 4 , an inter cooler 5 and an intake manifold 6 which are arranged at a halfway portion of an air suction passage 2 of an engine 1 .
  • the tube actuator 4 and a DPF 8 are arranged at a half portion of an exhaust passage 7 of the engine 1 .
  • a first exhaust gas recirculation pipe 9 is connected with a downstream side of exhaust gas of the DPF 8 and an upstream side of suction air of the tube actuator 4 .
  • the EGR cooler 10 and an exhaust gas recirculation valve 11 are arranged at a halfway portion of the first exhaust gas recirculation pipe 9 , which is a pipe for refluxing a part of exhaust gas having passed the DPF 8 to the suction side of the engine.
  • the exhaust gas recirculation device further has a second exhaust gas recirculation pipe 12 and an exhaust gas recirculation valve 13 (EGR valve) which is arranged at a halfway portion of the second exhaust gas recirculation pipe 12 .
  • EGR valve exhaust gas recirculation valve 13
  • a part of exhaust gas of the engine is refluxed through the second exhaust gas recirculation pipe 12 directly to the suction side of the engine, immediately before passing the DPF 8 .
  • the pressure of exhaust gas flowing through the first exhaust gas recirculation pipe 9 can be lower than that of exhaust gas flowing through the second exhaust gas recirculation pipe 12 . In this case, the exhaust gas recirculation can be operated even when the engine 1 has a high load.
  • the EGR cooler 10 cools exhaust gas by coolant of the engine 1 , which is cooling liquid (for example, cooling water) in this embodiment.
  • coolant of the engine 1 which is cooling liquid (for example, cooling water) in this embodiment.
  • the EGR cooler 10 has multiple tubes 21 , multiple inner fins 22 , water side tanks 23 and gas side tanks 24 , which can be made of a stainless steel and integrated with each other by brazing, welding or the like.
  • the tube 21 defines therein an exhaust passage 21 a in which exhaust gas flows. Cooling water flows at the outer side of the tube 21 , and exhaust gas is heat-exchanged with cooling water through the tube 21 .
  • the tube 21 having a long side 21 c and a short side 21 d is provided with a flat-shaped cross section when being viewed from the exhaust gas flowing direction.
  • the multiple tubes 21 are stacked in a stacking direction (for example, up-down-direction in FIG. 3 ) which is perpendicular to the longitudinal direction (i.e., extension direction of long side 21 c ) of the tube 21 .
  • the outer wall surfaces of the tubes 21 which are adjacent to each other defines therebetween a cooling water passage 21 b through which cooling water flows between the adjacent tubes 21 .
  • Cooling water having flowed into the EGR cooler 10 is distributed and supplied for the tubes 21 by the one water side tank 23 . Cooling water having flowed through the cooling water passage 21 b between the tubes 21 are collected and retrieved by the other water side tank 23 .
  • the water side tanks 23 are arranged around the tubes 21 which are stacked, in the vicinity of the two ends (of exhaust gas flowing direction) of the tube 21 .
  • Each of the water side tanks 23 is provided with a cooling water port 23 a (as cooling water outlet or inlet).
  • the gas side tanks 24 are respectively arranged at the two ends (of exhaust gas flowing direction) of the tube 21 .
  • the gas side tanks 24 are connected with the first exhaust gas recirculation pipe 9 .
  • Exhaust gas is distributed and supplied for the tubes 21 , by the one gas side tank 24 .
  • the exhaust gas having been heat-exchanged is colleted and retrieved from the tubes 21 , by the other gas side tank 24 .
  • the inner fins 22 are respectively arranged in the tubes 21 , to improve the heat exchange between exhaust gas and cooling water.
  • the inner fin 22 can be fixed to the inner wall surface of the tube 21 .
  • the inner fin 22 being constructed of the offset fin, has a cross section (taken along a direction which is substantially perpendicular to exhaust gas flowing direction), which has a corrugated shape extending in the longitudinal direction of the tube 21 . That is, this cross section of the inner fin 22 has convex portions 31 which are respectively arranged at crest positions and trough positions of the corrugated shape which are alternately arranged. The convex portion 31 of the inner fin 22 is arranged to contact the inner wall surface of the tube 21 .
  • the inner fin 22 (offset fin) is partially lanced (cut and raised) to have multiple lanced segments 32 .
  • the lanced segments 32 are arrayed in the exhaust gas flowing direction, in such a manner that the adjacent lanced segments 32 offset from each other in the longitudinal direction of the tube 21 (i.e., longitudinal direction of inner fin 22 ).
  • the inner fin 22 can be provided with multiple rows (substantially in exhaust gas flowing direction) of the lanced segments 32 .
  • the interior of the tube 21 is divided into multiple passages which are substantially parallel to each other with respect to the longitudinal direction (extension direction of long side 21 a ) of the tube 21 .
  • the wall portions 33 of the lanced segments 32 which define therein the passage are arranged staggeringly in the longitudinal direction of the inner fin 22 .
  • an offset amount s it is desirable for an offset amount s to be substantially equal to a half of the passage height u, so that the heat transfer coefficient can become high and the gas resistance can become small.
  • the offset amount s and the passage height u are dimensions in the longitudinal direction of the longitudinal direction of fin 22 .
  • the lanced segments 32 which are adjacent to each other in the flowing direction of the exhaust gas deviate from each other at the offset amount s in the longitudinal direction (which is substantially perpendicular to flowing direction of exhaust gas) of the fin 22 .
  • the inner fin 22 can be shaped in such a manner that the convex portion 31 includes a linear portion or does not include a linear portion in the cross section (taken along a direction substantially perpendicular to exhaust gas flowing direction) of the inner fin 22 .
  • the dotted field C in this cross section of the inner fin 22 is positioned between the convex portions 31 which are arranged at the crest positions (or trough positions) and adjacent to each other in the longitudinal direction of inner fin 22 , and surrounded by the inner fin 22 and the tube 21 . That is, the dotted field C is positioned between the wall portions 33 (facing each other) of the two lanced segments 32 which are adjacent to each other in the longitudinal direction of the inner fin 22 , and surrounded by the inner fin 22 and the tube 21 .
  • the offset area T is an area of a part, which is defined in this cross section and surrounded by the wall portions 33 of the two lanced segments 32 which are adjacent to each other in the exhaust gas flowing direction and offset from each other in the longitudinal direction of inner fin 22 .
  • the inner fin 22 can be manufactured by a flat plate which is bent to have a corrugated shape by pressing and further lanced by pressing to form the segment 32 .
  • the lancing of the segment 32 can be performed in such a manner that slits are beforehand formed before the corrugated shape is provided and thereafter the raising is performed.
  • the inner fin 22 has the cross section with the corrugated shape is formed.
  • the lancing of segment 32 can be also performed in such a manner that the two surfaces of the flat plate are pressed by a press machine so that the cutting and raising are simultaneously performed.
  • the inner fin 22 can be also manufactured by rolling, or by a combination of rolling and pressing.
  • the performance of the EGR cooler 10 is related to the specifications of the inner fin 22 such as a fin pitch fp, a fin height fh and the like.
  • the fin pitch fp is a distance between central lines of the two convex portions 31 (which adjacent to each other) of one of a crest side and a trough side, in the corrugated cross section (taken along substantially perpendicular to exhaust gas flowing direction) of the inner fin 22 .
  • the fin height fh is a distance between the tops of the two convex portions 31 which are respectively positioned at the crest side and the trough side in this corrugated cross section.
  • the optimum specifications of the inner fin 22 are investigated in this embodiment.
  • experiments are performed for the EGR coolers 10 which are respectively provided with the various fin pitches fp and fin heights fh, to evaluate the pressure loss of the exhaust gas flowing in the tube 21 , the hydraulic resistance of cooling water flowing at the outer side of the tube 21 , the clogged degree of the tube 21 , and the heat radiating performance of the each EGR cooler 10 when exhaust gas and cooling water flow under a predetermined condition.
  • the optimum specifications of the inner fin 22 can be determined.
  • the predetermined condition is set in such a manner that the temperature Tg 1 at the exhaust gas inlet is equal to 400° C., the exhaust gas flow amount is equal to 30 g/s, the exhaust gas inlet pressure Pg 1 is equal to 50 kPa, the temperature Tw 1 at the cooling water inlet is equal to 80° C. and the flow amount of cooling water is equal to 10 L/min.
  • FIG. 7 shows the relation between the fin pitch height fh and a pressure loss ratio ( ⁇ Pg ratio).
  • the pressure loss is a difference between the exhaust gas pressure Pg 1 at the exhaust gas inlet of the water side tank 14 and the exhaust gas pressure Pg 2 at the exhaust gas outlet of the water side tank 14 .
  • the pressure loss ratio ( ⁇ Pg ratio) is a ratio (percentage) when the maximum value of the pressure loss at the various conditions is set as 100.
  • the offset fin 22 is provided with the plate thickness of about 0.2 mm, the fin pitch fp of about 5 mm or 7 mm, the length L (which is dimension in exhaust gas flowing direction and named segment length L later) of the lanced segment 32 of about 1 mm or 5 mm, and the curvature radius R (of convex portion 31 ) of about 0.2 mm.
  • the curves A-C shown in FIG. 7 indicating the relation between ⁇ Pg and fh, are obtained in such a manner that the build of the EGR cooler 10 has a fixed value (that is, size of water side tank 23 and that of gas side tank 24 are fixed) and the fin pitch fp and the segment length L are provided with different values.
  • the curve A is obtained in such a manner that the fin pitch fp is equal to about 5 mm and the segment length L is equal to about 1 mm.
  • the curve B is obtained in such a manner that the fin pitch fp is equal to about 5 mm and the segment length L is equal to about 5 mm.
  • the curve B is obtained in such a manner that the fin pitch fp is equal to about 7 mm and the segment length L is equal to about 5 mm.
  • the ascent variation ratio of the pressure loss when the fin height fh is smaller than or equal to 3.5 mm is larger that when the fin height fh is larger than 3.5 mm.
  • the pressure loss when fh is smaller than or equal to 3.5 mm is relatively large and the pressure loss when fh is larger than 3.5 mm is relatively small. Therefore, it is desirable for the fin height fh to be larger than 3.5 mm.
  • FIG. 8 shows the relation between the fin height fh and a hydraulic resistance ⁇ Pw which is a difference between a water pressure at the cooling water inlet 23 a of the water side tank 23 and the cooling water outlet 23 a thereof.
  • the relation shown in FIG. 8 is obtained with the inner fin 22 being provided with a same condition as that of FIG. 7 .
  • the hydraulic resistance ⁇ Pw tends to increase.
  • a water pump having a high performance becomes necessary to maintain the flowing amount of cooling water (in order to maintain cooling performance) when the hydraulic resistance ⁇ Pw becomes lager than or equal to 3 kPa.
  • the hydraulic resistance ⁇ Pw is substantially equal to 3.2 kPa in the case where the fin height fh is set as 12 mm.
  • the cost will become high. Therefore, it is desirable for the fin height fh to be smaller than or equal to 10 mm.
  • the offset amount s will become small.
  • the offset amount s will become excessively small when the fin pitch fp is smaller than or equal to about 2 mm.
  • the inner fin 22 will be susceptible to being clogged by coal in exhaust gas. Therefore, it is desirable for the fin pitch fp to be larger than 2 mm.
  • the offset amount s can be set to be larger than 0.5 mm, considering that the advantage sedimentation thickness of the PM (particulate matter) at the surface of the single lanced segment 32 is about 0.25 mm when about 8 hours has elapsed, as shown in FIGS. 13A and 13B . Thus, the clogging can be restricted.
  • the heat-radiating capacity of the inner fin 22 can be heightened, by shortening the segment length L.
  • the relation between the fin pitch fp and the heat-radiating capacity of the inner fin 22 in the case where the segment length L is provided with a minimum value is investigated.
  • the fin pitch fp is larger than about 16 mm, it is difficult for the EGR cooler 10 to be provided with the necessary heat-radiating capacity.
  • the fin pitch fp is smaller than or equal to 12 mm, which is an approximate maximum fin pitch for satisfying the performance required by the exhaust gas regulation, as shown in FIG. 14 .
  • FIG. 14 is an approximate maximum fin pitch for satisfying the performance required by the exhaust gas regulation
  • Q represents the heat radiating amount of the EGR cooler 10
  • V represents the capacity of the core (which contributes to heat-exchanging and includes exhaust gas passage and cooling water passage) of the EGR cooler 10 .
  • the relation between Q/V and fp (fin pitch) is determined with respectively setting the fin height fh as 12 mm (fh 12 ) and 3.6 mm (fh3.6) and setting the segment length L as 1 mm (L 1 ) and 10 mm (L 10 ).
  • the fin pitch fp and the fin height fh are in the range defined by the following formula (I).
  • the pressure loss of exhaust gas flowing in the tube 21 and the hydraulic resistance ⁇ Pw of cooling water flowing at the outer side of the tube 21 can be restricted, so that the tube 21 can be restricted from being clogged and the heat radiating capacity can be improved.
  • the optimum specifications of the inner fin 22 are determined according to different criterions and parameters from those of the above-described first embodiment.
  • the optimum specifications of the inner fin 22 are determined based on the relation between an equivalent circle diameter de and an EGR gas density ratio ⁇ .
  • the equivalent circle diameter de means a diameter of an equivalent circle into which the field C in the cross section (substantially perpendicular to exhaust gas flowing direction) of the inner fin 22 is converted.
  • the field C is positioned between the convex portions 31 which are arranged at the crest positions (or trough positions) and adjacent to each other, and surrounded by the inner fin 22 and the tube 21 .
  • the equivalent circle diameter de can be calculated by the following formula (2).
  • S represents an area (which corresponds to the cross section area of the circle and is calculated by ⁇ D 2 /4 wherein the circle diameter is represented by D) of the cross section of the exhaust gas passage.
  • W represents a length of a wetted perimeter corresponding to a circumference calculated by ⁇ D wherein the circle diameter is represented by D.
  • the length W is a length (that is, length of the part where the inner wall surface contacts exhaust gas) of the inner wall surface of the single gas passage defined by the inner fin 22 and the tube 21 .
  • FIG. 9 is a schematic sectional view of the inner fin 22 which is taken long the direction perpendicular to the exhaust gas flowing direction.
  • the half of the wetted perimeter length W/2 (corresponding to right half of the dotted field C shown in FIG. 6 , for example) is indicated by five parts w 1 -w 5 .
  • the half of the cross section area S/2 of the gas passage (corresponding to right half of the dotted field C shown in FIG. 6 , for example) is indicated by four parts a-d.
  • the equivalent circle diameter de can be determined according to the fin pitch fp, the fin height fh, the plate thickness t and the curvature radius R of the bent portion.
  • the EGR gas density ⁇ (having a unit of kg/m 3 , for example) is a factor considering both the cooling capacity of the EGR cooler 10 and the pressure loss, and can be calculated according to the following formula (12).
  • the filling factor of the EGR gas will become high when the EGR gas density ⁇ becomes large. Thus, the EGR rate can be increased.
  • Pg 2 represents an absolute pressure (Pa) of the gas outlet.
  • R represents a gas constant 287.05 J/kg ⁇ K.
  • Tg 2 represents a temperature (K) of the gas outlet.
  • FIG. 10 shows a relation between the equivalent circle diameter de and the EGR gas density ratio ( ⁇ ratio), which is a ratio when the maximum value of the EGR gas density ⁇ is set as 100%.
  • the relations shown in FIG. 10 are obtained with the gas inlet temperature Tg 1 of about 400° C., the gas flowing amount of about 30 g/s, the gas inlet pressure Pg 1 of about 50 kPa, the cooing water inlet temperature Tw 1 of about 80° C., the cooling water flowing amount of about 10 L/min, the fin plate thickness t of about 0.2 mm, the fin height fh of about 9 mm and the curvature radius of about 0.2 mm.
  • the curve D shown in FIG. 10 is measured when the segment length L is equal to about 1 mm
  • the curve E shown in FIG. 10 is measured when the segment length L is equal to about 5 mm.
  • the relation between the equivalent circle diameter de and the EGR gas density ratio can be indicated by a curve similar to the curve D.
  • the relation can be indicated by a curve similar to the curve E.
  • the ⁇ ratio can become larger than or equal to about 93% by setting the equivalent circle diameter de in the range of about 1.2 ⁇ de ⁇ 6.1
  • the ⁇ ratio can become larger than or equal to about 95% by setting the equivalent circle diameter de in the range of about 1.3 ⁇ de ⁇ 5.3
  • the ⁇ ratio can become larger than or equal to about 97% by setting the equivalent circle diameter de in the range of about 1.5 ⁇ de ⁇ 4.5.
  • the ⁇ ratio in the case of about 5 ⁇ L ⁇ 15, can become larger than or equal to about 93% by setting the equivalent circle diameter de in the range of about 1.0 ⁇ de ⁇ 4.3, the ⁇ ratio can become larger than or equal to about 95% by setting the equivalent circle diameter de in the range of about 1.1 ⁇ de ⁇ 4.0, and the ⁇ ratio can become larger than or equal to about 97% by setting the equivalent circle diameter de in the range of about 1.3 ⁇ de ⁇ 3.5.
  • segment length L and the equivalent circle diameter de and the like are provided with the unit of mm.
  • the relation shown in FIG. 10 is measured when the plate thickness t and the curvature radius R of the fin are equal to 0.2 mm.
  • This relation can be indicated by curves similar to the curves D and E, even when the plate thickness t and the curvature radius R are changed in the range which can be embodied.
  • this relation can be indicated by curves similar to the curves D and E′ when the plate thickness t and the curvature radius R are respectively changed in the range from 0.1 mm to 0.2 mm.
  • the optimum specifications of the inner fin 22 are determined according to different criterions and parameters from those of the above-described embodiments.
  • the optimum specifications of the inner fin 22 are determined based on the relation between the segment length L and the EGR gas density ratio ( ⁇ ratio).
  • FIG. 11 shows the relation between the segment length L and the EGR gas density ratio ( ⁇ ratio), which is a ratio when the maximum value of the EGR gas density ⁇ is set as 100%.
  • ⁇ ratio is a ratio when the maximum value of the EGR gas density ⁇ is set as 100%.
  • the relation shown in FIG. 11 is obtained with the same condition as that of FIG. 10 , excepting the fin height fh and the segment length L.
  • the curve F in FIG. 11 is calculated when fh ⁇ 7 and fp ⁇ 5, for example, when fh is equal to 4.6 and fp is equal to 4.5.
  • the EGR gas density ratio ( ⁇ ratio) can be larger than or equal to about 95%.
  • the ⁇ ratio can be larger than or equal to about 97%.
  • the ⁇ ratio can be larger than or equal to about 99%.
  • the curve G in FIG. 11 is calculated when fh ⁇ 7 and fp>5, for example, when fh is equal to about 4.6 and fp is equal to about 5.5.
  • the EGR gas density ratio ( ⁇ ratio) can be larger than or equal to about 95%.
  • the ⁇ ratio can be larger than or equal to about 97%.
  • the ⁇ ratio can be larger than or equal to about 99%.
  • the curve H in FIG. 11 is calculated when fh ⁇ 7 and fp ⁇ 5, for example, when fh is equal to about 9 and fp is equal to about 4.5.
  • the EGR gas density ratio ⁇ ratio
  • the segment length L is in the range of 0.5 ⁇ L ⁇ 50
  • the ⁇ ratio can be larger than or equal to about 95%.
  • the ⁇ ratio can be larger than or equal to about 97%.
  • the ⁇ ratio can be larger than or equal to about 99%.
  • the curve I in FIG. 11 is calculated when fh ⁇ 7 and fp>5, for example, when fh is equal to about 9 and fp is equal to about 5.5.
  • the EGR gas density ratio ( ⁇ ratio) can be larger than or equal to about 95%.
  • the ⁇ ratio can be larger than or equal to about 97%.
  • the ⁇ ratio can be larger than or equal to about 99%.
  • the fin pitch fp, the fin height fh, the segment length L and the like are provided with the unit of mm.
  • the relation shown in FIG. 11 is obtained when the plate thickness t and the curvature radius R of the inner fin 22 are equal to about 0.2 mm.
  • This relation can be indicated by curves similar to the curves F-I, even when the plate thickness t and the curvature radius R are changed in the range which can be embodied.
  • this relation can be indicated by curves similar to the curves F-I when the plate thickness t and the curvature radius R are respectively changed in the range from 0.1 mm to 0.2 mm.
  • the optimum specifications of the inner fin 22 are determined according to different criterions and parameters from those of the above-described embodiments.
  • the optimum specifications of the inner fin 22 are determined based on the relation between the EGR gas density ratio ( ⁇ ratio) and a function X using the equivalent circle diameter de, the segment length L and the fin height fh.
  • FIG. 12 shows the relation between the EGR gas density ratio ( ⁇ ratio) and the function X which can be indicated by the following formula (13).
  • FIG. 12 shows the calculation result a of the EGR gas density ratio ( ⁇ ratio) in the case where the fin pitch fp, the fin height fh and the segment length L are respectively provided with various values.
  • the curves in FIG. 10 are obtained in the case where the fin pitch fp has an arbitrary value while the segment length L and the fin height fh are provided with a fixed value.
  • the fin pitch fp is provided with a value in the substantial range from 1.5 mm to 14 mm, while the fin height fh is substantially equal to one of 3.6 mm, 4.6 mm, 5.6 mm, 7 mm, 9 mm and 12 mm and the segment length L is substantially equal to one of 1 mm and 10 mm.
  • Other measurement conditions of FIG. 12 are same as those of FIGS. 10 and 11 .
  • the curves indicating the relation between the EGR gas density ratio ( ⁇ ratio) and the function X show a similar tendency under different conditions.
  • the EGR gas density ratio ( ⁇ ratio) can be larger than or equal to about 93%.
  • the ⁇ ratio can be larger than or equal to about 95%.
  • the segment length L and the equivalent circle diameter de can be set so that the function X has a value in the substantial range of 1.3 ⁇ X ⁇ 3.5.
  • the ⁇ ratio can be larger than or equal to about 97%.
  • the size of the core of the exhaust gas heat exchanger can be reduced.
  • the function X and the like is provided with the unit of mm.
  • the relations shown in FIG. 12 are obtained when the plate thickness t and the curvature radius R of the fin are equal to about 0.2 mm. This relation can be indicated similarly to what is shown in FIG. 12 , even when the plate thickness t and the curvature radius R are changed in the range which can be embodied. For example, this relation can be indicated similarly when the plate thickness t and the curvature radius R are respectively changed in the range from 0.1 mm to 0.2 mm.
  • the exhaust gas heat exchanger according to the present invention can be also suitably used as an EGR cooler which is arranged at a halfway portion of the second exhaust gas recirculation pipe 12 through which a part of the exhaust gas of the engine 1 is returned directly to the suction side of the engine 1 before flowing through the DPF 8 .
  • the present invention can be also suitably used for the other exhaust gas heat exchanger made of a stainless steel or the like, other than the EGR cooler.
  • the present invention can be suitably used for the exhaust gas heat exchanger through which cooling water is heat-exchanged with exhaust gas discharged to the ambient air to be heated.

Landscapes

  • 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)
US11/827,409 2006-07-11 2007-07-11 Exhaust gas heat exchanger Abandoned US20080011464A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-190428 2006-07-11
JP2006190428 2006-07-11

Publications (1)

Publication Number Publication Date
US20080011464A1 true US20080011464A1 (en) 2008-01-17

Family

ID=38885132

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/827,409 Abandoned US20080011464A1 (en) 2006-07-11 2007-07-11 Exhaust gas heat exchanger

Country Status (3)

Country Link
US (1) US20080011464A1 (zh)
CN (1) CN101105374B (zh)
DE (1) DE102007031912A1 (zh)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090095456A1 (en) * 2007-10-04 2009-04-16 Ktm Kuhler Gmbh Plate heat exchanger
US20100031506A1 (en) * 2008-08-08 2010-02-11 Ruben Hartwig Method for producing steam generator tube walls consisting primarily of 9-12% martensitic chromium steels
US20100037872A1 (en) * 2008-08-18 2010-02-18 Gm Global Technology Operating, Inc. Preventing egr system soot contamination
EP2208550A2 (de) * 2009-01-17 2010-07-21 Mahle International GmbH Turbulenzblech
US20100319889A1 (en) * 2009-06-17 2010-12-23 Denso Corporation Heat exchanger for cooling high-temperature gas
US20100329895A1 (en) * 2009-06-24 2010-12-30 Robert Leroy Baker Multistage compressor installation
US20120211214A1 (en) * 2010-12-09 2012-08-23 Panasonic Avionics Corporation Heatsink Device and Method
US20120291993A1 (en) * 2011-05-18 2012-11-22 K&N Engineering, Inc. Intercooler system
US20140069625A1 (en) * 2004-07-23 2014-03-13 Ntnu Technology Transfer As Method and equipment for heat recovery
US20140238006A1 (en) * 2011-10-18 2014-08-28 Calsonic Kansei Corporation Exhaust gas heat exchanger
US20140318512A1 (en) * 2013-04-25 2014-10-30 Gm Global Technology Operations, Llc Exhaust gas recirculation cooler, system, and method thereof
US20160084582A1 (en) * 2014-09-22 2016-03-24 Mahle International Gmbh Heat exchanger
US20160236262A1 (en) * 2015-02-17 2016-08-18 Denso Corporation Offset Fin Manufacturing Method And Offset Fin Manufacturing Apparatus
US20160377350A1 (en) * 2015-06-29 2016-12-29 Honeywell International Inc. Optimized plate fin heat exchanger for improved compliance to improve thermal life
US9689628B2 (en) 2010-07-09 2017-06-27 Denso Corporation Oil cooler with inner fin
US20170184060A1 (en) * 2014-06-13 2017-06-29 Korens Co., Ltd. Heat exchanger having wave fin plate for reducing egr gas pressure difference
US9956654B2 (en) 2013-04-03 2018-05-01 Denso Corporation Method for manufacturing heat exchanger, and heat exchanger
US20180120034A1 (en) * 2016-11-01 2018-05-03 Ingersoll-Rand Company Bar and plate air-oil heat exchanger
US20180328317A1 (en) * 2017-05-11 2018-11-15 Hyundai Motor Company Water-cooled egr cooler, and the manufacturing method thereof
US20190063854A1 (en) * 2017-08-30 2019-02-28 Toyota Jidosha Kabushiki Kaisha Heat dissipation sheet and method for manufacturing heat dissipation sheet
US10392979B2 (en) 2015-06-30 2019-08-27 Tokyo Radiator Mfg. Co., Ltd. Inner fin for heat exchanger
US10458371B2 (en) * 2017-04-10 2019-10-29 Hyundai Motor Company EGR cooler
US10712097B2 (en) 2014-05-09 2020-07-14 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same
US11193722B2 (en) * 2018-05-01 2021-12-07 Dana Canada Corporation Heat exchanger with multi-zone heat transfer surface
US11280559B2 (en) * 2020-05-12 2022-03-22 Hanon Systems Dumbbell shaped plate fin
CN114485216A (zh) * 2022-01-10 2022-05-13 中国科学院理化技术研究所 辐射翅片式换热器及自由活塞斯特林发电机

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101697448B (zh) * 2009-10-24 2012-09-05 永济新时速电机电器有限责任公司 变流器功率模块双面水冷散热基板
CN103727830B (zh) * 2013-12-31 2015-08-05 成都恒润高新科技有限公司 一种热能回收换热器
JP6333571B2 (ja) * 2014-02-10 2018-05-30 三菱重工オートモーティブサーマルシステムズ株式会社 熱交換器用オフセットフィンおよびそれを用いた冷媒熱交換器
CN106332511A (zh) * 2015-06-18 2017-01-11 蔡承恩 复合式散热结构
FR3040478B1 (fr) * 2015-08-25 2017-12-15 Valeo Systemes Thermiques Echangeur de chaleur
US20180216519A1 (en) * 2017-02-02 2018-08-02 GM Global Technology Operations LLC Multiple Turbulator Heat Exchanger
KR102299349B1 (ko) * 2017-04-10 2021-09-08 현대자동차주식회사 차량용 egr 쿨러
CN109813144B (zh) * 2019-02-25 2020-07-31 温州冲亚电子科技有限公司 一种高效除污油水通用散热器

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4805693A (en) * 1986-11-20 1989-02-21 Modine Manufacturing Multiple piece tube assembly for use in heat exchangers
US5107922A (en) * 1991-03-01 1992-04-28 Long Manufacturing Ltd. Optimized offset strip fin for use in contact heat exchangers
US5625229A (en) * 1994-10-03 1997-04-29 Sumitomo Metal Industries, Ltd. Heat sink fin assembly for cooling an LSI package
US20010000879A1 (en) * 1988-08-12 2001-05-10 Masatsugu Sugawara Multi-flow type heat exchanger
US6247523B1 (en) * 1999-07-30 2001-06-19 Denso Corporation Exhaust gas heat exchanger
US20010047861A1 (en) * 2000-05-10 2001-12-06 Akihiro Maeda Brazing method, brazement, method of production of corrosion-resistant heat exchanger, and corrosion-resistant heat exchanger
US20020162646A1 (en) * 2001-03-13 2002-11-07 Haasch James T. Angled turbulator for use in heat exchangers
US20030019214A1 (en) * 2001-07-26 2003-01-30 Takanori Shibata Gas turbine installation
US20050097681A9 (en) * 2002-02-12 2005-05-12 Sylvain Kravtchenko Dye composition comprising an oxidation base of the diaminopyrazole type, a cationic oxidation base and a coupler
US20050121179A1 (en) * 2001-07-16 2005-06-09 Kazuhiro Shibagaki Exhaust gas heat exchanger
US20050247444A1 (en) * 2002-07-09 2005-11-10 Hajime Ohata Tube for heat exchanger
US20070017661A1 (en) * 2003-10-20 2007-01-25 Behr Gmbh & Co, Kg Heat exchanger
US20070056721A1 (en) * 2005-09-09 2007-03-15 Usui Kokusai Sangyo Kaisha Limited Heat exchanger tube
US20070119430A1 (en) * 2005-11-29 2007-05-31 Denso Corporation Intercooler
US20070119581A1 (en) * 2003-09-30 2007-05-31 Soichi Kato Heat exchanger tube
US7303002B2 (en) * 2004-09-08 2007-12-04 Usui Kokusai Sangyo Kaisha Limited Fin structure, heat-transfer tube having the fin structure housed therein, and heat exchanger having the heat-transfer tube assembled therein
US20100139897A1 (en) * 2005-04-29 2010-06-10 Stanley Chu Heat Exchangers with Turbulizers Having Convolutions of Varied Height

Patent Citations (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4805693A (en) * 1986-11-20 1989-02-21 Modine Manufacturing Multiple piece tube assembly for use in heat exchangers
US20010000879A1 (en) * 1988-08-12 2001-05-10 Masatsugu Sugawara Multi-flow type heat exchanger
US20020153131A1 (en) * 1988-08-12 2002-10-24 Calsonic Kansei Corporation Multi-flow type heat exchanger
US5107922A (en) * 1991-03-01 1992-04-28 Long Manufacturing Ltd. Optimized offset strip fin for use in contact heat exchangers
US5625229A (en) * 1994-10-03 1997-04-29 Sumitomo Metal Industries, Ltd. Heat sink fin assembly for cooling an LSI package
US6247523B1 (en) * 1999-07-30 2001-06-19 Denso Corporation Exhaust gas heat exchanger
US20010047861A1 (en) * 2000-05-10 2001-12-06 Akihiro Maeda Brazing method, brazement, method of production of corrosion-resistant heat exchanger, and corrosion-resistant heat exchanger
US20020162646A1 (en) * 2001-03-13 2002-11-07 Haasch James T. Angled turbulator for use in heat exchangers
US20050121179A1 (en) * 2001-07-16 2005-06-09 Kazuhiro Shibagaki Exhaust gas heat exchanger
US20050039436A1 (en) * 2001-07-26 2005-02-24 Hitachi, Ltd. Gas turbine installation
US20040065074A1 (en) * 2001-07-26 2004-04-08 Hitachi, Limited Gas turbine installation
US20030019214A1 (en) * 2001-07-26 2003-01-30 Takanori Shibata Gas turbine installation
US20060144034A1 (en) * 2001-07-26 2006-07-06 Hitachi, Ltd. Gas turbine installation
US20050097681A9 (en) * 2002-02-12 2005-05-12 Sylvain Kravtchenko Dye composition comprising an oxidation base of the diaminopyrazole type, a cationic oxidation base and a coupler
US20050247444A1 (en) * 2002-07-09 2005-11-10 Hajime Ohata Tube for heat exchanger
US20070119581A1 (en) * 2003-09-30 2007-05-31 Soichi Kato Heat exchanger tube
US20070017661A1 (en) * 2003-10-20 2007-01-25 Behr Gmbh & Co, Kg Heat exchanger
US7303002B2 (en) * 2004-09-08 2007-12-04 Usui Kokusai Sangyo Kaisha Limited Fin structure, heat-transfer tube having the fin structure housed therein, and heat exchanger having the heat-transfer tube assembled therein
US20100139897A1 (en) * 2005-04-29 2010-06-10 Stanley Chu Heat Exchangers with Turbulizers Having Convolutions of Varied Height
US20070056721A1 (en) * 2005-09-09 2007-03-15 Usui Kokusai Sangyo Kaisha Limited Heat exchanger tube
US20070119430A1 (en) * 2005-11-29 2007-05-31 Denso Corporation Intercooler

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
11/827,409 Equation Sheet, 1 page. *

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9732981B2 (en) * 2004-07-23 2017-08-15 Norsk Hydro Asa Method and equipment for heat recovery
US20140069625A1 (en) * 2004-07-23 2014-03-13 Ntnu Technology Transfer As Method and equipment for heat recovery
US8418752B2 (en) * 2007-10-04 2013-04-16 Mahle International Gmbh Plate heat exchanger having a turbulence generator
US20090095456A1 (en) * 2007-10-04 2009-04-16 Ktm Kuhler Gmbh Plate heat exchanger
US8713794B2 (en) * 2008-08-08 2014-05-06 Alstom Technology Ltd. Method for producing steam generator tube walls consisting primarily of 9-12% martensitic chromium steels
US20100031506A1 (en) * 2008-08-08 2010-02-11 Ruben Hartwig Method for producing steam generator tube walls consisting primarily of 9-12% martensitic chromium steels
US20100037872A1 (en) * 2008-08-18 2010-02-18 Gm Global Technology Operating, Inc. Preventing egr system soot contamination
EP2208550A2 (de) * 2009-01-17 2010-07-21 Mahle International GmbH Turbulenzblech
US20100319889A1 (en) * 2009-06-17 2010-12-23 Denso Corporation Heat exchanger for cooling high-temperature gas
US8708036B2 (en) 2009-06-17 2014-04-29 Denso Corporation Heat exchanger for cooling high-temperature gas
US20100329895A1 (en) * 2009-06-24 2010-12-30 Robert Leroy Baker Multistage compressor installation
US8376718B2 (en) * 2009-06-24 2013-02-19 Praxair Technology, Inc. Multistage compressor installation
US9689628B2 (en) 2010-07-09 2017-06-27 Denso Corporation Oil cooler with inner fin
US20120211214A1 (en) * 2010-12-09 2012-08-23 Panasonic Avionics Corporation Heatsink Device and Method
US20120291993A1 (en) * 2011-05-18 2012-11-22 K&N Engineering, Inc. Intercooler system
US20140238006A1 (en) * 2011-10-18 2014-08-28 Calsonic Kansei Corporation Exhaust gas heat exchanger
US9103250B2 (en) * 2011-10-18 2015-08-11 Calsonic Kansei Corporation Exhaust gas heat exchanger
US9956654B2 (en) 2013-04-03 2018-05-01 Denso Corporation Method for manufacturing heat exchanger, and heat exchanger
US20140318512A1 (en) * 2013-04-25 2014-10-30 Gm Global Technology Operations, Llc Exhaust gas recirculation cooler, system, and method thereof
US9109547B2 (en) * 2013-04-25 2015-08-18 GM Global Technology Operations LLC Exhaust gas recirculation cooler, system, and method thereof
US10712097B2 (en) 2014-05-09 2020-07-14 Panasonic Intellectual Property Management Co., Ltd. Offset fin and heat exchanger having same
US20170184060A1 (en) * 2014-06-13 2017-06-29 Korens Co., Ltd. Heat exchanger having wave fin plate for reducing egr gas pressure difference
US9951724B2 (en) * 2014-06-13 2018-04-24 Korens Co., Ltd. Heat exchanger having wave fin plate for reducing EGR gas pressure difference
US20160084582A1 (en) * 2014-09-22 2016-03-24 Mahle International Gmbh Heat exchanger
US10060684B2 (en) * 2014-09-22 2018-08-28 Mahle International Gmbh Heat exchanger
US20160236262A1 (en) * 2015-02-17 2016-08-18 Denso Corporation Offset Fin Manufacturing Method And Offset Fin Manufacturing Apparatus
US10220431B2 (en) * 2015-02-17 2019-03-05 Denso Corporation Offset fin manufacturing method and offset fin manufacturing apparatus
US20160377350A1 (en) * 2015-06-29 2016-12-29 Honeywell International Inc. Optimized plate fin heat exchanger for improved compliance to improve thermal life
US10392979B2 (en) 2015-06-30 2019-08-27 Tokyo Radiator Mfg. Co., Ltd. Inner fin for heat exchanger
US20180120034A1 (en) * 2016-11-01 2018-05-03 Ingersoll-Rand Company Bar and plate air-oil heat exchanger
US10458371B2 (en) * 2017-04-10 2019-10-29 Hyundai Motor Company EGR cooler
US20180328317A1 (en) * 2017-05-11 2018-11-15 Hyundai Motor Company Water-cooled egr cooler, and the manufacturing method thereof
US10253730B2 (en) * 2017-05-11 2019-04-09 Hyundai Motor Company Water-cooled EGR cooler, and the manufacturing method thereof
US20190063854A1 (en) * 2017-08-30 2019-02-28 Toyota Jidosha Kabushiki Kaisha Heat dissipation sheet and method for manufacturing heat dissipation sheet
US11193722B2 (en) * 2018-05-01 2021-12-07 Dana Canada Corporation Heat exchanger with multi-zone heat transfer surface
US11280559B2 (en) * 2020-05-12 2022-03-22 Hanon Systems Dumbbell shaped plate fin
CN114485216A (zh) * 2022-01-10 2022-05-13 中国科学院理化技术研究所 辐射翅片式换热器及自由活塞斯特林发电机

Also Published As

Publication number Publication date
CN101105374A (zh) 2008-01-16
DE102007031912A1 (de) 2008-02-07
CN101105374B (zh) 2010-12-08

Similar Documents

Publication Publication Date Title
US20080011464A1 (en) Exhaust gas heat exchanger
JP4240136B2 (ja) 排気熱交換器
US7614443B2 (en) Heat exchanger tube
US8069905B2 (en) EGR gas cooling device
US8544454B2 (en) Heat exchanger for a motor vehicle
US7478630B2 (en) Device and method for cooling exhaust gas
US7866305B2 (en) Flow channel, heat exchanger, exhaust gas recirculation system, charge air supply system, use of a heat exchanger
US7628199B2 (en) Heat exchanger, in particular air/air cooler
US8651170B2 (en) Exhaust gas heat exchanger
US9163880B2 (en) Heat exchanger
US7942137B2 (en) Heat exchanger
US6408939B1 (en) Double heat exchanger
US20090133860A1 (en) Heat exchanger
US7011142B2 (en) Finned plate heat exchanger
US20080264609A1 (en) Heat exchanger for exhaust gas cooling; method for operating a heat exchanger; system with a heat exchanger for exhaust gas cooling
US20070227715A1 (en) Heat exchanger
US20080185130A1 (en) Heat exchanger with extruded cooling tubes
CN102213554A (zh) 热交换器及其制造方法
US20050077033A1 (en) Device for exchanging heat and method of manufacturing such device
KR20150043388A (ko) 열교환기 인서트
EP2037200A2 (en) Composite heat exchanger
US20080000627A1 (en) Heat exchanger
JP4069570B2 (ja) 排気熱交換器
JP2007064606A (ja) Ｅｇｒクーラーの熱交換用チューブ
US20130075071A1 (en) Heat Exchanger

Legal Events

Date Code Title Description
AS Assignment

Owner name: DENSO CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:OOFUNE, YUU;HAYASHI, TAKAYUKI;REEL/FRAME:019755/0545

Effective date: 20070717

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION