US20150292812A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- US20150292812A1 US20150292812A1 US14/437,956 US201214437956A US2015292812A1 US 20150292812 A1 US20150292812 A1 US 20150292812A1 US 201214437956 A US201214437956 A US 201214437956A US 2015292812 A1 US2015292812 A1 US 2015292812A1
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- US
- United States
- Prior art keywords
- partition wall
- heat
- heat transfer
- exchange body
- heat exchange
- 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
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Classifications
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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
- 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
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
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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
- F02M26/32—Liquid-cooled heat exchangers
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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
- 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
- F28D7/10—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 one within the other, e.g. concentrically
- F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
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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
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/04—Constructions of heat-exchange apparatus characterised by the selection of particular materials of ceramic; of concrete; of natural stone
Definitions
- the present invention is related to a heat exchanger.
- Patent Document 1 discloses a heat exchanger having: a first fluid flow portion formed by a honeycomb structure having plural cells through which a heated element of a first fluid flows; and a second fluid flow portion provided in the outer circumferential portion of the first fluid flow portion. Coolant flows through the second fluid flow portion, so that heat is taken from the heated element flowing through the first fluid flow portion, which cools the heated element.
- Patent Document 2 discloses an air-cooling semiconductor heat sink having: cooling surfaces having a radial shape; and cooling surfaces having a concentric shape about an axis and integrated with the cooling surfaces having a radial shape. Conceivably, the cooling surfaces having a radial shape and the cooling surfaces having a concentric shape disclosed in Patent Document 2 easily ensure a heat radiation area, and they are effectively used in combination with the heat exchanger disclosed in Patent Document 1.
- Patent Document 1 International Publication No. WO 2011/071161
- a heat exchanger described in the present specification includes: a heat exchange body through which a fluid serving as a cooled object passes; and a coolant passage which is provided in at least one of a central portion and an outer circumferential portion of the heat exchange body, and through which a coolant exchanging heat with the heat exchange body flows, wherein the heat exchange body includes: a first heat transfer means which extends from a central portion to an outer circumferential portion; and a second heat transfer means which extends in a circumferential direction, and which intersects the first heat transfer means. Further, a heat transfer efficiency of the first heat transfer means is greater than that of the second heat transfer means.
- the heat transfer efficiency is understood as a value obtained by multiplying a heat conductivity, which is a physical property value of a material of which the heat exchange body is made, by a thickness of one partition wall.
- the heat transfer efficiency, of the heat flow in the radial direction, namely, a heat transfer path extending to the coolant passage provided in the central portion or the outer circumferential portion of the heat exchange body, is set high, thereby improving the heat conductive property. Accordingly, the good heat conductive property is ensured in the heat exchanger, which can effectively cool the cooled object.
- the first heat transfer means may be first partition walls extending radially from a central portion to an outer circumferential portion of the heat exchange body
- the second heat transfer means may be second partition walls having a concentric shape
- a thickness of the first partition wall may be larger than that of the second partition wall.
- the walls having a concentric shape, that is, the second partition walls can increase the contact area with the fluid serving as the cooled object.
- each heat transfer efficiency of such partition walls having a concentric shape has to be smaller than that of partition walls extending radially, that is, the first partition walls. Therefore, the thickness of the first partition wall is set larger than that of the second partition wall, so that the heat transfer efficiency of the first partition walls serving as the first heat transfer means is made greater than that of second partition walls.
- the first heat transfer means may be first partition walls extending radially from a central portion to an outer circumferential portion of the heat exchange body
- the second heat transfer means may be second partition walls having a concentric shape
- a heat conductive property of a material of the first partition wall may be greater than that of a material of the second partition wall.
- the walls having a concentric shape, that is, the second partition walls can increase the contact area with the fluid serving as the cooled object.
- each heat transfer efficiency of such partition walls having a concentric shape has to be smaller than that of partition walls extending radially, that is, the first partition walls.
- the first partition wall is made of the material having a heat conductive property greater than that of the material of which the second partition wall is made, so that the heat transfer efficiency of the first partition walls serving as the first heat transfer means is made greater than that of second partition walls.
- the first partition wall can be made of the material having a heat conductivity greater than that of the material of which the second partition wall is made.
- the first heat transfer means may be a first partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body
- the second heat transfer means may be a second partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body
- at least one of a thickness of the first partition wall and the second partition wall may include a portion having a thickness becoming smaller from the inlet side to an outlet side.
- the temperature of the fluid serving as the cooled object becomes higher as it comes closer to the inlet of the heat exchange body.
- the first partition wall or the second partition wall is made thicker as it is closer to the inlet, so that the heat is easily transferred to the coolant passage side, which improves the temperature efficiency.
- the first heat transfer means may be a first partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body
- the second heat transfer means may be a second partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body
- at least one of a thickness of the first partition wall and the second partition wall may include a portion having a thickness becoming larger from the inlet side to an outlet side.
- FIG. 1 is an explanatory view schematically illustrating a heat exchanger according to a first embodiment
- FIG. 2 is a sectional view taken along line A-A of FIG. 1 ;
- FIG. 3 is an explanatory view illustrating thicknesses of first partition walls and second partition walls
- FIG. 4 is an explanatory view illustrating a variation changing density of the second partition walls
- FIG. 5 is an explanatory view illustrating arrangements of second partition walls in the variation illustrated in FIG. 4 ;
- FIG. 6 is an explanatory view illustrating a heat exchanger according to a second embodiment
- FIGS. 7(A) to (C) are explanatory views illustrating a heat exchanger according to a third embodiment
- FIGS. 8(A) to (C) are explanatory views illustrating a heat exchanger according to a fourth embodiment
- FIG. 9 is an explanatory view illustrating a variation in which a cross section of a second partition wall has a rectangular shape
- FIG. 10 is an explanatory view illustrating a variation in which a cross section of a second partition wall has a spiral shape
- FIG. 11 is an explanatory view illustrating a variation in which a cross section of a second partition wall has an elliptic shape
- FIG. 12 is an explanatory view illustrating a variation in which coolant passages are provided in a central portion and an outer circumferential portion of a heat exchange body.
- FIG. 1 is an explanatory view schematically illustrating the heat exchanger 1 according to the first embodiment.
- FIG. 2 is a sectional view taken along line A-A of FIG. 1 .
- FIG. 3 is an explanatory view illustrating thicknesses of partition walls provided in the heat exchanger 1 .
- the heat exchanger 1 includes an EGR pipe 2 through which the EGR gas flows.
- the EGR pipe is a tube material made from stainless steel (SUS).
- the EGR pipe 2 can also be made from another material such as aluminum.
- the heat exchanger 1 includes a housing member 3 , an end portion 3 a of which is joined to an end portion 2 a of the EGR pipe 2 , and which forms a coolant passage 4 in the outer circumferential portion of the EGR pipe 2 .
- the housing member 3 is also made from stainless steel (SUS).
- the housing member 3 includes a coolant inlet 3 b 1 for introducing the coolant into the coolant passage 4 and a coolant outlet 3 b 2 for discharging the coolant from the coolant passage 4 .
- the coolant may be any fluid, but it is cooling water in the present embodiment.
- An outer wall of the housing member 3 is provided with stays 3 c.
- a heat exchange body 5 arranged to abut with the inner circumferential wall surface 2 b of the EGR pipe 2 is accommodated within the EGR pipe 2 .
- the fluid serving as a cooled object, that is, the EGR gas passes through the heat exchange body 5 in the present embodiment.
- the heat exchange body 5 is made of a silicon carbide ceramic (SiC).
- the ceramic material has an efficient heat conductivity and can exert a high corrosion resistance. Therefore, the ceramic material having a high heat conductivity is preferably suitable for materials of the heat exchange body arranged within the EGR pipe and a covering member.
- the heat exchange body 5 is formed into a cylindrical shape, and a passage through which the gas can pass is formed.
- the heat exchange body 5 can exchange heat from the coolant flowing into the coolant passage 4 through the EGR pipe 2 . That is, when the EGR gas passes through the heat exchange body 5 , heat is exchanged between the EGR gas and the coolant through the heat exchange body 5 and the EGR pipe 2 , so the EGR gas is cooled.
- the heat exchange body 5 has first partition walls 5 a , which radially extends from a central portion 6 toward the outer circumferential portion, and which serves as a first heat transfer means extending from the central portion 6 toward the outer circumferential portion. Further, the heat exchange body 5 has second partition walls 5 b , which have concentric shapes, and which serve as a second heat transfer means extending in the circumferential direction and intersecting the first partition walls 5 a .
- the central portion 6 is not required to be positioned perfectly at the center of the heat exchange body 5 .
- the first partition wall 5 a has only to form a heat transfer path from the inside to the outside.
- the second partition wall 5 b has only to be shaped with a portion continuous in the circumferential direction.
- its cross section perpendicular to the flowing direction of the fluid may have a circular shape, an ellipse shape, or a rectangular shape. Further, it is not required to have a full ring shape, and it may have an open ring shape.
- Such a second partition wall 5 b intersects the first partition wall 5 a , so that the strength of the heat exchange body 5 can be improved. Further, the provision of the second partition wall 5 b can increase the contact area with the fluid, thereby improving the temperature efficiency.
- the thickness T 1 of the first partition wall 5 a is larger than the thickness T 2 of the second partition wall 5 b .
- a change in the thickness between the first partition wall 5 a and the second partition wall 5 b makes the heat transfer efficiency of the first heat transfer means, that is, the first partition wall 5 a greater than that of the second heat transfer means, that is, the second partition wall 5 b .
- the first partition wall 5 a is thickened and the heat transfer path extending toward the coolant passage 4 is thickened, so the heat transfer efficiency can increase. Supposing the second partition wall 5 b is thickened, the pressure loss increases correspondingly.
- the second partition wall 5 b is so thin as to reduce the pressure loss, thereby contributing to the improvement in the heat efficiency.
- the second partition walls 5 b can be thinned one by one and the number thereof can be increased.
- the increase in the number of the second partition walls 5 b can further increase the contact area with the fluid.
- the temperature efficiency is further improved.
- the increase in the pressure loss can be suppressed by thinning the second partition walls 5 b .
- thinning the second partition walls 5 b one by one in association with the increase in the number of the second partition walls 5 b is also convenient for satisfaction of the relationship between the thickness of the first partition wall 5 a and the thickness of the second partition wall 5 b . Also, thinning the second partition wall 5 b provides an advantage in ensuring the flow passage area for the EGR gas.
- the EGR pipe having a cylindrical shape accommodates a heat exchange body having square cells
- the combination of the first partition walls 5 a extending radially and the second partition walls 5 b having a concentric shape can overcome the disadvantages, which are concerned in a case of employing the square cells.
- Such a heat exchanger 1 includes cone members 8 in the upstream side and the downstream side of the EGR pipe 2 .
- the cone member 8 in the upstream side is a member serving as an introduction portion for introducing the EGR gas into the EGR pipe 2 .
- the cone member 8 in the downstream side is a member serving as a discharging portion for the EGR gas in the EGR pipe 2 .
- the cone member 8 is joined to the housing member 3 by brazing such that a large diameter side covers the end portion 3 a of the housing member 3 .
- the front end portion of the cone member 8 is joined with a flange 9 member by brazing.
- the upstream side of the heat exchanger 1 is connected to an exhaust manifold of the engine by the flange 9 .
- the downstream side of the heat exchanger 1 is connected to an intake pipe. Additionally, the heat exchanger 1 is attached to the engine body by the stays 3 c provided on the outer wall of the housing member 3 .
- FIG. 4 is an explanatory view illustrating the variation changing the density of the second partition walls.
- FIG. 5 is an explanatory view illustrating the arrangements of the second partition walls in the variation illustrated in FIG. 4 .
- Plural second partition walls 5 b are arranged concentrically.
- Ln indicates the distance between the adjacent second partition walls 5 b .
- n is a natural number becoming larger from the central portion 6 to the outer circumferential portion.
- the distance Ln becomes larger toward the outer circumferential portion. That is, the second partition walls 5 b are arranged more densely as they are closer to the central portion 6 . Accordingly, the fluid, that is, the EGR gas flows more easily as it is closer to the outer circumferential portion side.
- the coolant passage 4 is provided in the outer circumferential portion. Therefore, in order to efficiently cool the EGR gas, it is desired that a large amount of the EGR gas flows into the outer circumference portion close to the coolant passage 4 . For this reason, the second partition walls 5 b are densely arranged near the central portion 6 side, so that the amount of the EGR gas flowing into the outer circumferential portion is larger than that of the EGR gas flowing into the central portion, which can improve the temperature efficiency.
- the portion where the second partition walls 5 b are arranged densely has only to be formed in a region close to the central portion 6 .
- FIG. 6 is an explanatory view illustrating a heat exchanger 20 according to the second embodiment.
- FIG. 6 corresponds to FIG. 2 describing the first embodiment.
- the heat exchanger 20 according to the second embodiment and the heat exchanger 1 according to the first embodiment. That is, the heat conductive property of the material of a first partition wall 25 a is greater than that of the material of the second partition wall 5 b .
- the thickness of a second partition wall 25 b is the same as that of the first partition wall 25 a .
- Other components are the same, so common components are designated with the same reference numerals in the drawings and descriptions of those components will be omitted.
- the first partition wall 25 a is made of a ceramic with a high heat conductivity.
- the second partition wall 25 b is made of a typical ceramic, that is, a ceramic with a heat conductivity (heat conductive property) inferior to that of the material of the first partition wall 25 a .
- heat taken from the fluid by the first partition walls 25 a and the second partition walls 25 b is easily transferred through the first partition walls 25 a to the coolant passage 4 .
- the thickness of the first partition wall 25 a can be the same as that of the second partition wall 25 b . It is therefore possible to reduce the pressure loss.
- FIG. 7(A) is an explanatory view of the heat exchanger 30 according to the third embodiment when viewed from an inlet side.
- FIG. 7(B) is a sectional view taken along line B-B of FIG. 7(A) .
- FIG. 7(C) is an explanatory view of the heat exchanger 30 according to the third embodiment when viewed from an outlet side.
- a first partition wall 35 a corresponding to the first heat transfer means extends from the inlet side to the outlet side of the EGR gas in a heat exchange body 35 .
- the thickness becomes smaller from the inlet side to the outlet side. That is, the thickness Tin in the inlet side >the thickness Tout in the outlet side.
- the EGR gas flowing into the heat exchange body 35 becomes higher as it comes closer to the inlet side. Therefore, in order to transfer heat toward the coolant passage 4 in the inlet side, the thickness Tin in the inlet side is larger than the thickness Tout in the outlet side. This can effectively cool the EGR gas.
- the thickness of the first partition wall 35 a is changed.
- a second partition wall 35 b extending from the inlet side to the outlet side of the EGR gas in the heat exchange body 35 can become thinner from the inlet side to the outlet side.
- FIG. 8(A) is an explanatory view of the heat exchanger 40 according to the fourth embodiment when viewed from an inlet side.
- FIG. 8(B) is a sectional view taken along line C-C of FIG. 8(A) .
- FIG. 8(C) is an explanatory view of the heat exchanger 40 according to the fourth embodiment when viewed from an outlet side.
- a first partition wall 45 a corresponding to the first heat transfer means extends from the inlet side to the outlet side of the EGR gas in a heat exchange body 45 .
- the thickness becomes lager from the inlet side to the outlet side. That is, the thickness Tin in the inlet side ⁇ the thickness Tout in the outlet side.
- the temperature of the EGR gas is high and the volume of the EGR gas is large in the vicinity of the inlet side, so the narrow flow passage area greatly influences on the pressure loss, which increases the pressure loss. For this reason, the thickness Tin in the inlet side is smaller than the thickness Tout in the outlet side. This can effectively cool the fluid. Further, the outlet side is made thick, so the deterioration in the temperature efficiency is suppressed.
- the thickness of the first partition wall 45 a is changed.
- a second partition wall 45 b extending from the inlet side to the outlet side of the EGR gas in the heat exchange body 45 can become thicker from the inlet side to the outlet side.
- the fourth embodiment is incompatible with the third embodiment, and any one can be selected depending on which is considered as important.
- FIG. 9 illustrates a heat exchanger 50 in which a cross section of a second partition wall 55 b has a rectangular shape.
- the heat exchanger 50 includes an EGR pipe 52 , a housing 53 , and a coolant passage 54 , and each cross section thereof has a rectangular shape.
- a heat exchange body 55 having first partition walls 55 a and the second partition walls 55 b is included. Even in such a case of providing rectangular cross-sections, the same arrangements as the first embodiment to the fourth embodiment can be employed.
- FIG. 10 illustrates a heat exchanger 60 in which a cross section of a second shape partition wall has a spiral shape.
- the heat exchanger 60 includes the EGR pipe 2 , the housing 3 , and the coolant passage 4 . Further, a heat exchange body 65 having first partition walls 65 a intersecting second partition walls 65 b having a spiral shape is included. Even in such a case where the cross section of the second partition wall 65 b has a spiral shape, the same arrangements as the first embodiment to the third embodiment can be employed.
- FIG. 11 illustrates a heat exchanger 70 in which a cross section of a second partition wall has an elliptic shape.
- the heat exchanger 70 includes an EGR pipe 72 , a housing 73 , and a coolant passage 74 , and each cross section thereof has an elliptic shape.
- a heat exchange body 75 having first partition walls 75 a and second partition walls 75 b is included. Even in such a case of providing elliptic cross-sections, the same arrangements as the first embodiment to the third embodiment can be employed.
- FIG. 12 illustrates a heat exchanger 80 in which coolant passages are provided in the central portion and the outer circumferential portion of the heat exchange body.
- the heat exchanger 80 includes a coolant passage 11 at the central portion, and in addition to the coolant passage 4 located at the outer circumferential portion. Even in such a case, the same arrangements as the first embodiment to the third embodiment can be employed. It is thus possible to effectively transfer heat to the coolant passage 4 and the coolant passage 11 , thereby cooling the EGR gas.
Abstract
A heat exchanger includes: a heat exchange body through which a fluid serving as a cooled object passes; and a coolant passage which is provided in at least one of a central portion and an outer circumferential portion of the heat exchange body, and through which a coolant exchanging heat with the heat exchange body flows, wherein the heat exchange body includes: a first heat transfer means which extends from a central portion to an outer circumferential portion; and a second heat transfer means which extends in a circumferential direction, and which intersects the first heat transfer means, a heat transfer efficiency of the first heat transfer means is greater than that of the second heat transfer means.
Description
- The present invention is related to a heat exchanger.
- Conventionally, various heat exchangers are known. For example,
Patent Document 1 discloses a heat exchanger having: a first fluid flow portion formed by a honeycomb structure having plural cells through which a heated element of a first fluid flows; and a second fluid flow portion provided in the outer circumferential portion of the first fluid flow portion. Coolant flows through the second fluid flow portion, so that heat is taken from the heated element flowing through the first fluid flow portion, which cools the heated element. Also,Patent Document 2 discloses an air-cooling semiconductor heat sink having: cooling surfaces having a radial shape; and cooling surfaces having a concentric shape about an axis and integrated with the cooling surfaces having a radial shape. Conceivably, the cooling surfaces having a radial shape and the cooling surfaces having a concentric shape disclosed inPatent Document 2 easily ensure a heat radiation area, and they are effectively used in combination with the heat exchanger disclosed inPatent Document 1. - [Patent Document 1] International Publication No. WO 2011/071161
- [Patent Docuemnt 2] Japanese Unexamined Patent Application Publication No. 2003-100974
- However, as for the combination of the above cooling surfaces having a radial shape and the cooling surfaces having a concentric shape, there is room for further improvement in heat transfer efficiency (heat conductive property) in consideration of the arrangements of the coolant and the heated element serving as a cooled object.
- It is thus an object to ensure a good heat conductive property in a heat exchanger disclosed in the present specification.
- To solve the problem, a heat exchanger described in the present specification includes: a heat exchange body through which a fluid serving as a cooled object passes; and a coolant passage which is provided in at least one of a central portion and an outer circumferential portion of the heat exchange body, and through which a coolant exchanging heat with the heat exchange body flows, wherein the heat exchange body includes: a first heat transfer means which extends from a central portion to an outer circumferential portion; and a second heat transfer means which extends in a circumferential direction, and which intersects the first heat transfer means. Further, a heat transfer efficiency of the first heat transfer means is greater than that of the second heat transfer means. Here, the heat transfer efficiency is understood as a value obtained by multiplying a heat conductivity, which is a physical property value of a material of which the heat exchange body is made, by a thickness of one partition wall.
- The heat transfer efficiency, of the heat flow in the radial direction, namely, a heat transfer path extending to the coolant passage provided in the central portion or the outer circumferential portion of the heat exchange body, is set high, thereby improving the heat conductive property. Accordingly, the good heat conductive property is ensured in the heat exchanger, which can effectively cool the cooled object.
- The first heat transfer means may be first partition walls extending radially from a central portion to an outer circumferential portion of the heat exchange body, the second heat transfer means may be second partition walls having a concentric shape, and a thickness of the first partition wall may be larger than that of the second partition wall. The walls having a concentric shape, that is, the second partition walls can increase the contact area with the fluid serving as the cooled object. On the other hand, each heat transfer efficiency of such partition walls having a concentric shape has to be smaller than that of partition walls extending radially, that is, the first partition walls. Therefore, the thickness of the first partition wall is set larger than that of the second partition wall, so that the heat transfer efficiency of the first partition walls serving as the first heat transfer means is made greater than that of second partition walls.
- The first heat transfer means may be first partition walls extending radially from a central portion to an outer circumferential portion of the heat exchange body, the second heat transfer means may be second partition walls having a concentric shape, and a heat conductive property of a material of the first partition wall may be greater than that of a material of the second partition wall. As mentioned above, the walls having a concentric shape, that is, the second partition walls can increase the contact area with the fluid serving as the cooled object. On the other hand, each heat transfer efficiency of such partition walls having a concentric shape has to be smaller than that of partition walls extending radially, that is, the first partition walls. Therefore, the first partition wall is made of the material having a heat conductive property greater than that of the material of which the second partition wall is made, so that the heat transfer efficiency of the first partition walls serving as the first heat transfer means is made greater than that of second partition walls. In order to have different heat conductive properties, there can be difference in the heat conductivity between the material of which the first partition wall is made and that of which the second partition wall. That is, the first partition wall can be made of the material having a heat conductivity greater than that of the material of which the second partition wall is made.
- The first heat transfer means may be a first partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body, the second heat transfer means may be a second partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body, at least one of a thickness of the first partition wall and the second partition wall may include a portion having a thickness becoming smaller from the inlet side to an outlet side. The temperature of the fluid serving as the cooled object becomes higher as it comes closer to the inlet of the heat exchange body. Thus, the first partition wall or the second partition wall is made thicker as it is closer to the inlet, so that the heat is easily transferred to the coolant passage side, which improves the temperature efficiency.
- The first heat transfer means may be a first partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body, the second heat transfer means may be a second partition wall extending from an inlet side to an outlet side of a fluid serving as a cooled object in the heat exchange body, and at least one of a thickness of the first partition wall and the second partition wall may include a portion having a thickness becoming larger from the inlet side to an outlet side. It is an embodiment to preferentially reduce the pressure loss. In the vicinity of the inlet of the heat exchange body, the temperature of the fluid is high, the volume thereof is large. For this reason, the narrow flow passage area greatly influences on the pressure loss, which increases the pressure loss. Therefore, the first partition wall or the second partition wall is made thinner as it is closer to the inlet, thereby reducing the pressure loss, and it is made thicker as it is closer to the outlet, thereby preventing a decrease in the temperature efficiency.
- According to a heat exchanger disclosed in the present specification, it is possible to ensure a good heat conductive property.
-
FIG. 1 is an explanatory view schematically illustrating a heat exchanger according to a first embodiment; -
FIG. 2 is a sectional view taken along line A-A ofFIG. 1 ; -
FIG. 3 is an explanatory view illustrating thicknesses of first partition walls and second partition walls; -
FIG. 4 is an explanatory view illustrating a variation changing density of the second partition walls; -
FIG. 5 is an explanatory view illustrating arrangements of second partition walls in the variation illustrated inFIG. 4 ; -
FIG. 6 is an explanatory view illustrating a heat exchanger according to a second embodiment; -
FIGS. 7(A) to (C) are explanatory views illustrating a heat exchanger according to a third embodiment; -
FIGS. 8(A) to (C) are explanatory views illustrating a heat exchanger according to a fourth embodiment; -
FIG. 9 is an explanatory view illustrating a variation in which a cross section of a second partition wall has a rectangular shape; -
FIG. 10 is an explanatory view illustrating a variation in which a cross section of a second partition wall has a spiral shape; -
FIG. 11 is an explanatory view illustrating a variation in which a cross section of a second partition wall has an elliptic shape; and -
FIG. 12 is an explanatory view illustrating a variation in which coolant passages are provided in a central portion and an outer circumferential portion of a heat exchange body. - Hereinafter, embodiments according to the present invention will be described with reference to the accompanying drawings. However, a dimension and a ratio of each component illustrated in the drawings may not correspond to the reality. Also, details may be omitted in some drawings.
- First, a
heat exchanger 1 according to the first embodiment will be described with reference toFIGS. 1 to 3 . Theheat exchanger 1, which can employ various types of fluids serving as cooled objects, is incorporated into an exhaust gas recirculation device equipped with an internal combustion engine in the first embodiment, and is used as an EGR cooler for cooling the EGR (Exhaust Gas Recirculation) gas.FIG. 1 is an explanatory view schematically illustrating theheat exchanger 1 according to the first embodiment.FIG. 2 is a sectional view taken along line A-A ofFIG. 1 .FIG. 3 is an explanatory view illustrating thicknesses of partition walls provided in theheat exchanger 1. - The
heat exchanger 1 includes an EGRpipe 2 through which the EGR gas flows. The EGR pipe is a tube material made from stainless steel (SUS). - The
EGR pipe 2 can also be made from another material such as aluminum. Theheat exchanger 1 includes ahousing member 3, anend portion 3 a of which is joined to anend portion 2 a of theEGR pipe 2, and which forms acoolant passage 4 in the outer circumferential portion of theEGR pipe 2. Thehousing member 3 is also made from stainless steel (SUS). Thehousing member 3 includes a coolant inlet 3b 1 for introducing the coolant into thecoolant passage 4 and a coolant outlet 3b 2 for discharging the coolant from thecoolant passage 4. The coolant may be any fluid, but it is cooling water in the present embodiment. An outer wall of thehousing member 3 is provided withstays 3 c. - A
heat exchange body 5 arranged to abut with the innercircumferential wall surface 2 b of theEGR pipe 2 is accommodated within theEGR pipe 2. The fluid serving as a cooled object, that is, the EGR gas passes through theheat exchange body 5 in the present embodiment. Theheat exchange body 5 is made of a silicon carbide ceramic (SiC). The ceramic material has an efficient heat conductivity and can exert a high corrosion resistance. Therefore, the ceramic material having a high heat conductivity is preferably suitable for materials of the heat exchange body arranged within the EGR pipe and a covering member. Theheat exchange body 5 is formed into a cylindrical shape, and a passage through which the gas can pass is formed. Theheat exchange body 5 can exchange heat from the coolant flowing into thecoolant passage 4 through theEGR pipe 2. That is, when the EGR gas passes through theheat exchange body 5, heat is exchanged between the EGR gas and the coolant through theheat exchange body 5 and theEGR pipe 2, so the EGR gas is cooled. - Referring to
FIG. 2 , theheat exchange body 5 hasfirst partition walls 5 a, which radially extends from acentral portion 6 toward the outer circumferential portion, and which serves as a first heat transfer means extending from thecentral portion 6 toward the outer circumferential portion. Further, theheat exchange body 5 hassecond partition walls 5 b, which have concentric shapes, and which serve as a second heat transfer means extending in the circumferential direction and intersecting thefirst partition walls 5 a. Herein, thecentral portion 6 is not required to be positioned perfectly at the center of theheat exchange body 5. Thefirst partition wall 5 a has only to form a heat transfer path from the inside to the outside. That is, it has only to extend in the radial direction, and it may be partly wave-shaped or may be curved. On the other hand, thesecond partition wall 5 b has only to be shaped with a portion continuous in the circumferential direction. As for thesecond partition wall 5 b, its cross section perpendicular to the flowing direction of the fluid may have a circular shape, an ellipse shape, or a rectangular shape. Further, it is not required to have a full ring shape, and it may have an open ring shape. Such asecond partition wall 5 b intersects thefirst partition wall 5 a, so that the strength of theheat exchange body 5 can be improved. Further, the provision of thesecond partition wall 5 b can increase the contact area with the fluid, thereby improving the temperature efficiency. - Referring now to
FIGS. 2 and 3 , the thickness T1 of thefirst partition wall 5 a is larger than the thickness T2 of thesecond partition wall 5 b. Thus, in the first embodiment, a change in the thickness between thefirst partition wall 5 a and thesecond partition wall 5 b makes the heat transfer efficiency of the first heat transfer means, that is, thefirst partition wall 5 a greater than that of the second heat transfer means, that is, thesecond partition wall 5 b. Thus, thefirst partition wall 5 a is thickened and the heat transfer path extending toward thecoolant passage 4 is thickened, so the heat transfer efficiency can increase. Supposing thesecond partition wall 5 b is thickened, the pressure loss increases correspondingly. However, in the first embodiment, thesecond partition wall 5 b is so thin as to reduce the pressure loss, thereby contributing to the improvement in the heat efficiency. Herein, thesecond partition walls 5 b can be thinned one by one and the number thereof can be increased. The increase in the number of thesecond partition walls 5 b can further increase the contact area with the fluid. As a result, the temperature efficiency is further improved. Even in a case of increasing the number of thesecond partition walls 5 b, the increase in the pressure loss can be suppressed by thinning thesecond partition walls 5 b. In such a way, thinning thesecond partition walls 5 b one by one in association with the increase in the number of thesecond partition walls 5 b is also convenient for satisfaction of the relationship between the thickness of thefirst partition wall 5 a and the thickness of thesecond partition wall 5 b. Also, thinning thesecond partition wall 5 b provides an advantage in ensuring the flow passage area for the EGR gas. - Herein, a description will be given of comparison between the thickness of the
first partition wall 5 a and the thickness of thesecond partition wall 5 b in more detail. Even if thefirst partition wall 5 a is partly thinned and its thickness is smaller than that of an arbitrary position of thesecond partition wall 5 b, the average thickness in thefirst partition wall 5 a has only to be larger than that in thesecond partition wall 5 b. - Further, if the EGR pipe having a cylindrical shape accommodates a heat exchange body having square cells, it might be difficult to maintain the square shape of the cell or the cell size might be reduced in the vicinity of the EGR pipe. This results in clogging easily, and there is a possibility to reduce the amount of the EGR gas flowing into the cells located at the outermost circumferential portion and to reduce the cooling efficiency. The combination of the
first partition walls 5 a extending radially and thesecond partition walls 5 b having a concentric shape can overcome the disadvantages, which are concerned in a case of employing the square cells. - Such a
heat exchanger 1 includes cone members 8 in the upstream side and the downstream side of theEGR pipe 2. The cone member 8 in the upstream side is a member serving as an introduction portion for introducing the EGR gas into theEGR pipe 2. The cone member 8 in the downstream side is a member serving as a discharging portion for the EGR gas in theEGR pipe 2. The cone member 8 is joined to thehousing member 3 by brazing such that a large diameter side covers theend portion 3 a of thehousing member 3. The front end portion of the cone member 8 is joined with aflange 9 member by brazing. The upstream side of theheat exchanger 1 is connected to an exhaust manifold of the engine by theflange 9. Also, the downstream side of theheat exchanger 1 is connected to an intake pipe. Additionally, theheat exchanger 1 is attached to the engine body by thestays 3 c provided on the outer wall of thehousing member 3. - A description will now be given of a variation according to the first embodiment with reference to
FIGS. 4 and 5 .FIG. 4 is an explanatory view illustrating the variation changing the density of the second partition walls.FIG. 5 is an explanatory view illustrating the arrangements of the second partition walls in the variation illustrated inFIG. 4 . - Plural
second partition walls 5 b are arranged concentrically. Herein, Ln indicates the distance between the adjacentsecond partition walls 5 b. n is a natural number becoming larger from thecentral portion 6 to the outer circumferential portion. The distance Ln becomes larger toward the outer circumferential portion. That is, thesecond partition walls 5 b are arranged more densely as they are closer to thecentral portion 6. Accordingly, the fluid, that is, the EGR gas flows more easily as it is closer to the outer circumferential portion side. In the first embodiment, thecoolant passage 4 is provided in the outer circumferential portion. Therefore, in order to efficiently cool the EGR gas, it is desired that a large amount of the EGR gas flows into the outer circumference portion close to thecoolant passage 4. For this reason, thesecond partition walls 5 b are densely arranged near thecentral portion 6 side, so that the amount of the EGR gas flowing into the outer circumferential portion is larger than that of the EGR gas flowing into the central portion, which can improve the temperature efficiency. - Additionally, as for the arrangements of the distance Ln in the whole, Ln−1<Ln may not be satisfied. In short, the portion where the
second partition walls 5 b are arranged densely has only to be formed in a region close to thecentral portion 6. - Next, a second embodiment will be described with reference to
FIG. 6 .FIG. 6 is an explanatory view illustrating aheat exchanger 20 according to the second embodiment.FIG. 6 corresponds toFIG. 2 describing the first embodiment. There are following differences between theheat exchanger 20 according to the second embodiment and theheat exchanger 1 according to the first embodiment. That is, the heat conductive property of the material of afirst partition wall 25 a is greater than that of the material of thesecond partition wall 5 b. Moreover, the thickness of asecond partition wall 25 b is the same as that of thefirst partition wall 25 a. Other components are the same, so common components are designated with the same reference numerals in the drawings and descriptions of those components will be omitted. - The
first partition wall 25 a is made of a ceramic with a high heat conductivity. On the other hand, thesecond partition wall 25 b is made of a typical ceramic, that is, a ceramic with a heat conductivity (heat conductive property) inferior to that of the material of thefirst partition wall 25 a. Thus, heat taken from the fluid by thefirst partition walls 25 a and thesecond partition walls 25 b is easily transferred through thefirst partition walls 25 a to thecoolant passage 4. Unlike the first embodiment, in theheat exchanger 20 according to the second embodiment, the thickness of thefirst partition wall 25 a can be the same as that of thesecond partition wall 25 b. It is therefore possible to reduce the pressure loss. - Next, a description will be given of a
heat exchanger 30 according to the third embodiment with reference toFIGS. 7(A) to (C).FIG. 7(A) is an explanatory view of theheat exchanger 30 according to the third embodiment when viewed from an inlet side.FIG. 7(B) is a sectional view taken along line B-B ofFIG. 7(A) .FIG. 7(C) is an explanatory view of theheat exchanger 30 according to the third embodiment when viewed from an outlet side. - A
first partition wall 35 a corresponding to the first heat transfer means extends from the inlet side to the outlet side of the EGR gas in aheat exchange body 35. The thickness becomes smaller from the inlet side to the outlet side. That is, the thickness Tin in the inlet side >the thickness Tout in the outlet side. The EGR gas flowing into theheat exchange body 35 becomes higher as it comes closer to the inlet side. Therefore, in order to transfer heat toward thecoolant passage 4 in the inlet side, the thickness Tin in the inlet side is larger than the thickness Tout in the outlet side. This can effectively cool the EGR gas. Additionally, in the example illustrated inFIGS. 7(A) to (C), the thickness of thefirst partition wall 35 a is changed. Herein, instead of thefirst partition wall 35 a or in conjunction therewith, asecond partition wall 35 b extending from the inlet side to the outlet side of the EGR gas in theheat exchange body 35 can become thinner from the inlet side to the outlet side. - Next, a description will be given of a
heat exchanger 40 according to the fourth embodiment with reference toFIGS. 8(A) to (C).FIG. 8(A) is an explanatory view of theheat exchanger 40 according to the fourth embodiment when viewed from an inlet side.FIG. 8(B) is a sectional view taken along line C-C ofFIG. 8(A) .FIG. 8(C) is an explanatory view of theheat exchanger 40 according to the fourth embodiment when viewed from an outlet side. - A
first partition wall 45 a corresponding to the first heat transfer means extends from the inlet side to the outlet side of the EGR gas in aheat exchange body 45. The thickness becomes lager from the inlet side to the outlet side. That is, the thickness Tin in the inlet side <the thickness Tout in the outlet side. This makes it possible to reduce the pressure loss in the inlet. The temperature of the EGR gas is high and the volume of the EGR gas is large in the vicinity of the inlet side, so the narrow flow passage area greatly influences on the pressure loss, which increases the pressure loss. For this reason, the thickness Tin in the inlet side is smaller than the thickness Tout in the outlet side. This can effectively cool the fluid. Further, the outlet side is made thick, so the deterioration in the temperature efficiency is suppressed. Additionally, in the example illustrated inFIGS. 8(A) to (C), the thickness of thefirst partition wall 45 a is changed. Herein, instead of thefirst partition wall 45 a or in conjunction therewith, asecond partition wall 45 b extending from the inlet side to the outlet side of the EGR gas in theheat exchange body 45 can become thicker from the inlet side to the outlet side. - In addition, the fourth embodiment is incompatible with the third embodiment, and any one can be selected depending on which is considered as important.
- Next, various variations will be described.
-
FIG. 9 illustrates aheat exchanger 50 in which a cross section of asecond partition wall 55 b has a rectangular shape. Like the first embodiment, theheat exchanger 50 includes anEGR pipe 52, ahousing 53, and acoolant passage 54, and each cross section thereof has a rectangular shape. Further, aheat exchange body 55 havingfirst partition walls 55 a and thesecond partition walls 55 b is included. Even in such a case of providing rectangular cross-sections, the same arrangements as the first embodiment to the fourth embodiment can be employed. - Next,
FIG. 10 illustrates aheat exchanger 60 in which a cross section of a second shape partition wall has a spiral shape. Like the first embodiment, theheat exchanger 60 includes theEGR pipe 2, thehousing 3, and thecoolant passage 4. Further, aheat exchange body 65 havingfirst partition walls 65 a intersectingsecond partition walls 65 b having a spiral shape is included. Even in such a case where the cross section of thesecond partition wall 65 b has a spiral shape, the same arrangements as the first embodiment to the third embodiment can be employed. - Next,
FIG. 11 illustrates aheat exchanger 70 in which a cross section of a second partition wall has an elliptic shape. Like the first embodiment, theheat exchanger 70 includes anEGR pipe 72, ahousing 73, and acoolant passage 74, and each cross section thereof has an elliptic shape. Further, aheat exchange body 75 havingfirst partition walls 75 a andsecond partition walls 75 b is included. Even in such a case of providing elliptic cross-sections, the same arrangements as the first embodiment to the third embodiment can be employed. - Next,
FIG. 12 illustrates aheat exchanger 80 in which coolant passages are provided in the central portion and the outer circumferential portion of the heat exchange body. Theheat exchanger 80 includes acoolant passage 11 at the central portion, and in addition to thecoolant passage 4 located at the outer circumferential portion. Even in such a case, the same arrangements as the first embodiment to the third embodiment can be employed. It is thus possible to effectively transfer heat to thecoolant passage 4 and thecoolant passage 11, thereby cooling the EGR gas. - While the exemplary embodiments of the present invention have been illustrated in detail, the present invention is not limited to the above-mentioned embodiments, and other embodiments, variations and modifications may be made without departing from the scope of the present invention. For example, it can be used for applications other than the EGR cooler.
- 1, 20, 30, 40, 50, 60, and 70 heat exchanger
- 2 EGR pipe
- 3, 53, 73 housing
- 4, 54, 74 coolant passage
- 5, 25, 55, 65, 75 heat exchange body
- 5 a, 25 a, 55 a, 65 a, 75 a first partition wall
- 5 b, 25 b, 55 b, 65 b, 75 b second partition wall
Claims (5)
1. A heat exchanger comprising:
a heat exchange body through which a fluid serving as a cooled object passes; and
a coolant passage which is provided in at least one of a central portion and an outer circumferential portion of the heat exchange body, and through which a coolant exchanging heat with the heat exchange body flows,
wherein
the heat exchange body includes:
a first heat transfer portion which extends from the central portion to the outer circumferential portion; and
a second heat transfer portion which extends in a circumferential direction, and which intersects the first heat transfer portion,
a heat transfer efficiency of the first heat transfer portion moans is greater than that of the second heat transfer portion.
2. The heat exchanger of claim 1 , wherein
the first heat transfer portion is first partition walls extending radially from the central portion to the outer circumferential portion of the heat exchange body,
the second heat transfer portion is second partition walls having a concentric shape,
a thickness of the first partition wall is larger than that of the second partition wall.
3. The heat exchanger of claim 1 , wherein
the first heat transfer portion is first partition walls extending radially from the central portion to the outer circumferential portion of the heat exchange body,
the second heat transfer portion is second partition walls having a concentric shape,
a heat conductive property of a material of the first partition wall is greater than that of a material of the second partition wall.
4. The heat exchanger of claim 1 , wherein
the first heat transfer portion is a first partition wall extending from an inlet side to an outlet side of the fluid serving as the cooled object in the heat exchange body,
the second heat transfer portion is a second partition wall extending from the inlet side to the outlet side of the fluid serving as the cooled object in the heat exchange body,
at least one of the first partition wall and the second partition wall includes a portion having a thickness becoming smaller from the inlet side to an outlet side.
5. The heat exchanger of claim 1 , wherein
the first heat transfer portion is a first partition wall extending from an inlet side to an outlet side of the fluid serving as the cooled object in the heat exchange body,
the second heat transfer portion is a second partition wall extending from the inlet side to the outlet side of the fluid serving as the cooled object in the heat exchange body,
at least one of the first partition wall and the second partition wall includes a portion having a thickness becoming larger from the inlet side to an outlet side.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2012/077641 WO2014064812A1 (en) | 2012-10-25 | 2012-10-25 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150292812A1 true US20150292812A1 (en) | 2015-10-15 |
Family
ID=50544209
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/437,956 Abandoned US20150292812A1 (en) | 2012-10-25 | 2012-10-25 | Heat exchanger |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150292812A1 (en) |
EP (1) | EP2913616A4 (en) |
JP (1) | JP6075381B2 (en) |
CN (1) | CN104736959B (en) |
WO (1) | WO2014064812A1 (en) |
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US20190093599A1 (en) * | 2017-09-27 | 2019-03-28 | Toyota Jidosha Kabushiki Kaisha | Exhaust heat recovery unit |
US20190263240A1 (en) * | 2016-06-17 | 2019-08-29 | Robert Bosch Gmbh | Electrical axle drive for a vehicle |
CN110314708A (en) * | 2018-03-30 | 2019-10-11 | 日本碍子株式会社 | Heat exchanger |
US20220252353A1 (en) * | 2021-02-09 | 2022-08-11 | Ngk Insulators, Ltd. | Heat exchange member, heat exchanger and heat conductive member |
US11549393B2 (en) * | 2019-02-18 | 2023-01-10 | Safran Aero Boosters Sa | Air-oil heat exchanger |
US11555661B2 (en) * | 2018-01-04 | 2023-01-17 | Ngk Insulators, Ltd. | Heat exchanging member and heat exchanger |
US11591950B2 (en) * | 2018-01-05 | 2023-02-28 | Ngk Insulators, Ltd. | Heat exchanging member, heat exchanger and heat exchanger with purifier |
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JP2015224797A (en) * | 2014-05-26 | 2015-12-14 | カルソニックカンセイ株式会社 | Exhaust heat recovery device and method for manufacturing the same |
JP2016125797A (en) * | 2015-01-08 | 2016-07-11 | 東京窯業株式会社 | Honeycomb structure |
KR102520578B1 (en) * | 2016-04-13 | 2023-04-10 | 어플라이드 머티어리얼스, 인코포레이티드 | Device for exhaust gas cooling |
JP7184629B2 (en) * | 2018-03-30 | 2022-12-06 | 日本碍子株式会社 | Heat exchanger |
WO2022190573A1 (en) | 2021-03-11 | 2022-09-15 | 日本碍子株式会社 | Heat exchange member and heat exchanger using this heat exchange member, and method for manufacturing this heat exchange member |
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Also Published As
Publication number | Publication date |
---|---|
JPWO2014064812A1 (en) | 2016-09-05 |
EP2913616A4 (en) | 2015-12-02 |
JP6075381B2 (en) | 2017-02-08 |
EP2913616A1 (en) | 2015-09-02 |
CN104736959B (en) | 2017-07-11 |
WO2014064812A1 (en) | 2014-05-01 |
CN104736959A (en) | 2015-06-24 |
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Legal Events
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |