US20170343302A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
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- US20170343302A1 US20170343302A1 US15/535,793 US201515535793A US2017343302A1 US 20170343302 A1 US20170343302 A1 US 20170343302A1 US 201515535793 A US201515535793 A US 201515535793A US 2017343302 A1 US2017343302 A1 US 2017343302A1
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- Prior art keywords
- opening
- heat exchanger
- fluid
- fin
- plates
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- 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.)
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
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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
- 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
- F28D9/0012—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 apparatus having an annular form
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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
- 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
- F28D9/0043—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 the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
- F01N2240/02—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a heat exchanger
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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
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
Definitions
- the present disclosure relates to a heat exchanger.
- Patent Document 1 There has been known an exhaust heat recovery device that is provided with a heat exchanger to exchange heat between exhaust gas from an internal combustion engine as a high-temperature fluid and a low-temperature fluid, and recovers exhaust heat (see Patent Document 1 below).
- the heat exchanger described in Patent Document 1 is a stacked plate heat exchanger including a plurality of stacked plates having a flowing space through which the low-temperature fluid flows.
- the plate of the heat exchanger described in Patent Document 1 includes a convex portion projecting from an outer surface of the plate.
- Patent Document 1 International Publication WO2014/014080
- heat exchangers are required to achieve improvement in heat exchange rate from a high-temperature fluid to a low-temperature fluid, and a heat exchanger may be desired that achieves a greater heat exchange rate than that of the heat exchanger described in Patent Document 1.
- a heat exchanger allowing an improved heat exchange rate from a high-temperature fluid to a low-temperature fluid.
- One aspect of the present disclosure is a heat exchanger to exchange heat between a first fluid and a second fluid.
- the heat exchanger comprises a plurality of plates and a fin.
- the plurality of plates comprise a flow path through which the first fluid flows.
- the fin couples mutually adjacent plates among the plurality of plates. Also, the fin comprises at least one first portion and at least one second portion.
- the first portion is a wall surface that comprises at least one first opening.
- the second portion is a wall surface that is paired with the first portion, and is different from the first portion.
- the second portion comprises a second opening paired with a corresponding one of the at least one first opening.
- the paired first portion and second portion provide a wave-shaped section.
- the fin is such that the first portion and the second portion each are arranged in a direction orthogonal to a flow direction of the second fluid.
- the fin comprises at least one opening pair that is a pair of the first opening and the second opening. The at least one opening pair has a non-overlapping positional relationship in which the paired first opening and second opening are at least partially non-overlapping along the flow direction of the second fluid.
- the fin of the one aspect of the present disclosure extends such that the wall surfaces are orthogonal to the flow direction of the second fluid.
- the second fluid contacts the entire wall surfaces of the fin, and a large contact area can be obtained.
- the second fluid that has passed through the first opening of the fin strikes an area of the second portion facing the first opening.
- a flow of the second fluid is disturbed; thus, it is possible to inhibit formation of a boundary layer in the area of the second portion struck by the second fluid.
- the heat exchanger of the one aspect of the present disclosure enables to inhibit formation of the boundary layer between the second fluid and the fin, and enables an efficient heat transfer from the second fluid to the first fluid.
- the heat exchanger of the one aspect of the present disclosure enables further improvement in heat exchange rate from the high-temperature fluid to the low-temperature fluid.
- the heat exchanger of the one aspect of the present disclosure may be configured as a heat exchanger in which cylindrical plates are stacked in an axial direction.
- the fin of one aspect of the present disclosure may be arranged along a circumferential direction of the plates.
- the flow direction of the second fluid may be in a direction along a radial direction.
- the first fluid flows along the circumferential direction of the plates.
- the flow direction of the second fluid may be in a direction orthogonal to a flow direction of the first fluid.
- it is achieved that the flow direction of the second fluid is in a direction orthogonal to the flow direction of the first fluid over all radial directions of the plates, that is, over an entire flow area of the second fluid.
- the paired first opening and second opening may be entirely non-overlapping along the flow direction of the second fluid.
- the heat exchanger of the one aspect of the present disclosure enables to inhibit, over a larger area, formation of the boundary layer around a region of the second portion facing the first opening.
- the fin in the heat exchanger of the one aspect of the present disclosure may be such that all the opening pairs each have a non-overlapping positional relationship.
- the heat exchanger of the one aspect of the present disclosure enables to inhibit, over a much larger area, formation of the boundary layer around a region of the second portion facing the first opening.
- FIG. 1 is a perspective view showing a schematic outer appearance of an exhaust heat recovery device in an embodiment.
- FIG. 2 is a sectional view of the exhaust heat recovery device in a valve closed condition taken along a line II-II in FIG. 1 .
- FIG. 3 is a side view of a heat exchanger.
- FIG. 4 is a perspective view showing an outer appearance of a plate and a fin.
- FIG. 5 is a perspective view showing an outer appearance of the fin.
- FIG. 6 is a top view of the fin.
- first communicating portion 39 . . . second communicating portion, 40 . . . first cylindrical portion, 42 . . . second cylindrical portion, 44 . . . inflow pipe, 46 . . . outflow pipe, 50 . . . fin, 52 . . . first portion, 54 . . . second portion, 56 . . . first opening, 58 . . . first opening portion, 60 . . . second opening, 62 . . . second opening portion, 64 , 66 . . . gap, 80 . . . introducing member, 102 . . . valve body, 104 . . . valve seat, 108 . . . mesh member, 110 . . . internal combustion engine, 112 . . . exhaust gas (second fluid), 114 . . . coolant (first fluid)
- An exhaust heat recovery device 1 shown in FIG. 1 is mounted in a moving body that comprises an internal combustion engine 110 .
- the exhaust heat recovery device 1 exchanges heat between exhaust gas 112 from the internal combustion engine 110 as a high-temperature fluid and a coolant 114 of the internal combustion engine 110 as a low-temperature fluid, to thereby recover heat from the exhaust gas 112 .
- the exhaust gas 112 of the present embodiment is one example of “a second fluid” of the present disclosure
- the coolant 114 is one example of “a first fluid” of the present disclosure.
- the coolant 114 of the present embodiment may be cooling water or may be oil.
- the exhaust heat recovery device 1 of the present embodiment comprises an exhaust portion 2 , a shell member 4 , a heat exchanging portion 6 (see FIG. 2 ), an inflow portion 8 (see FIG. 2 ), and a valve 10 .
- the exhaust portion 2 comprises a path to guide exhaust gas 112 from the internal combustion engine 110 toward downstream.
- the shell member 4 is a member covering an outside of the exhaust portion 2 .
- the heat exchanging portion 6 comprises a heat exchanger 30 (see FIG. 2 ) arranged between the exhaust portion 2 and the shell member 4 , and performs heat exchange between the exhaust gas 112 as the high-temperature fluid and the low-temperature fluid that flows inside plates 32 of the heat exchanger 30 .
- the inflow portion 8 is a portion through which the exhaust gas 112 flows from the exhaust portion 2 into the heat exchanging portion 6 .
- the valve 10 which is a known valve that opens and closes a path, is arranged downstream from the inflow portion 8 along a flow path of the exhaust gas 112 in the exhaust portion 2 .
- the exhaust portion 2 comprises an exhaust pipe 12 .
- the exhaust pipe 12 is a cylindrical member.
- the exhaust gas 112 from the internal combustion engine 110 flows into the exhaust pipe 12 .
- the shell member 4 comprises an exhaust pipe 14 , an outer shell member 20 , a lid member 22 , and a retaining member 24 .
- the exhaust pipe 14 is a generally cylindrical member comprising an upstream end 16 as one end having an opening with an inner diameter greater than an outer diameter of the exhaust pipe 12 .
- an exhaust downstream end 18 which is an end opposite to an upstream end, of the exhaust pipe 12 is arranged in a non-contact state with the shell member 4 .
- the outer shell member 20 is a cylindrical member with an inner diameter greater than a diameter of the exhaust pipe 12 .
- a downstream end of the outer shell member 20 is coupled to the upstream end 16 of the exhaust pipe 14 .
- the lid member 22 closes an upstream opening of the outer shell member 20 along the flow path of the exhaust gas 112 in the exhaust pipe 12 .
- the outer shell member 20 , the lid member 22 , and the exhaust pipe 12 provide a heat exchanging chamber 28 that is an annular space surrounded by the outer shell member 20 , the lid member 22 , and the exhaust pipe 12 .
- the heat exchanger 30 arranged in the heat exchanging chamber 28 is a heat exchanger, in which the coolant 114 flows and which is arranged so as to cover an outer circumference of the exhaust pipe 12 .
- the heat exchanger 30 of the present embodiment comprises a plurality of plates 32 - 1 to 32 -N, an inflow pipe 44 , an outflow pipe 46 , and a plurality of fins 50 - 1 to 50 -M. That is, the heat exchanger 30 is a so-called stacked-plate heat exchanger.
- a symbol N which is an identifier denoting the number of the plates 32 , is a positive integer of 2 or more.
- a symbol M in the present embodiment is an identifier denoting the number of the fins 50 .
- the symbol M is, for example, a positive integer smaller by “1” than N.
- Each of the plates 32 comprises a flow path through which the coolant 114 flows.
- the fin 50 couples mutually adjacent plates 32 among the plurality of plates 32 .
- the inflow pipe 44 is a pipe to cause the coolant 114 from outside the heat exchanger 30 to flow into one plate 32 .
- the outflow pipe 46 is a pipe to cause the coolant 114 to flow out of the heat exchanger 30 from one plate 32 .
- each of the plates 32 comprises a first plate portion 34 and a second plate portion 36 .
- the first plate portion 34 is a ring-shaped member.
- the first plate portion 34 comprises a wall portion protruding in a same direction from a periphery of the first plate portion 34 .
- the second plate portion 36 is a ring-shaped member.
- the second plate portion 36 comprises a wall portion protruding in a same direction from a periphery of the second plate portion 36 .
- Each of the plates 32 is formed by engaging the wall portion of the first plate portion 34 with the wall portion of the second plate portion 36 .
- Each of the plates 32 comprises a gap between an inner surface of the first plate portion 34 and an inner surface of the second plate portion 36 .
- the gap functions as a flowing space in which the low-temperature fluid flows, that is, a flow path of the coolant 114 .
- Each of the plates 32 comprises a first communicating portion 38 and a second communicating portion 39 .
- the first communicating portion 38 comprises a flow path through which the coolant 114 from the inflow pipe 44 flows into an adjacent plate 32 from upstream toward downstream along the flow path of the exhaust gas 112 in the exhaust portion 2 .
- the second communicating portion 39 comprises a flow path through which the coolant 114 flows into an adjacent plate 32 from downstream to the outflow pipe 46 along the flow path of the exhaust gas 112 in the exhaust portion 2 .
- Each of the first communicating portion 38 and the second communicating portion 39 of the present embodiment comprises a first cylindrical portion 40 and a second cylindrical portion 42 .
- the first cylindrical portion 40 is a cylindrical portion that is erected from an opening provided to the first plate portion 34 in a direction opposite to that of the wall portion.
- the second cylindrical portion 42 is a cylindrical portion that is erected from a periphery of an opening provided to the second plate portion 36 in a direction opposite to that of the wall portion.
- first cylindrical portions 40 provided to the first plate portion 34 and the second cylindrical portions 42 provided to the second plate portion 36 function as the first communicating portion 38 and the second communicating portion 39 .
- the second cylindrical portion 42 provided to the second plate portion 36 here means the second cylindrical portion 42 provided to the second plate portion 36 that is adjacent to an outer surface of the first plate portion 34 through the fin 50 .
- a configuration method of the first communicating portion 38 and the second communicating portion 39 is not limited to this, and any configuration may be employed in which these portions are configured to function as a flow path for the coolant 114 through the plates 32 .
- Each of the plates 32 is also arranged so as to cover the outer circumference of the exhaust pipe 12 .
- Each of the plates 32 is arranged so as to have a gap 64 between a center side periphery of the plate 32 in a radial direction thereof and an outer surface of the exhaust pipe 12 , the gap 64 being located along a radial direction of the exhaust pipe 12 .
- each of the plates 32 is arranged so as to have a gap 66 between an outer side periphery of the plate 32 in the radial direction thereof and an inner surface of the outer shell member 20 , the gap 66 being located along the radial direction of the exhaust pipe 12 .
- the exhaust gas 112 in the present embodiment flows in a direction from the outer surface of the exhaust pipe 12 toward the inner surface of the outer shell member 20 along a radial direction of the plate 32 .
- the fin 50 is a truncated arc member coupled to two plates 32 adjacent to each other. As shown in FIG. 5 and FIG. 6 , the fin 50 comprises first portions 52 - 1 to 52 -L and second portions 54 - 1 to 54 -L. In the fin 50 , the first portions 52 and the second portions 54 are coupled, to thereby provide a triangular wave-shaped section of the fin 50 in its entirety.
- a symbol “L” here is an integer of 1 or more.
- the first portions 52 are each a rectangular plate portion that functions as a wall surface of the fin 50 .
- the first portions 52 each comprise at least one first opening portion 58 having a first opening 56 .
- the first portions 52 each may have the first openings 56 arranged at equal intervals, or may have the first openings 56 arranged at unequal intervals.
- the second portions 54 are each a rectangular plate portion that is paired with the first portion 52 and functions as a wall surface different from the first portion 52 . Also, the second portions 54 each comprise at least one second opening portion 62 having a second opening 60 that is paired with the first opening 56 . In the present embodiment, the second portions each may have the second openings 60 arranged at equal intervals, or may have the second openings 60 arranged at unequal intervals.
- Areas of the individual first openings 56 , areas of the individual second openings 60 , a total area of the first openings 56 , and a total area of the second openings 60 may be appropriately determined in consideration of a pressure of the exhaust gas 112 .
- One side in a longitudinal direction of one of the first portions 52 is coupled to one side in a longitudinal direction of one of the second portions 54 .
- the other side in the longitudinal direction of the one of the first portions 52 is coupled to one side in a longitudinal direction of a different one of the second portions 54 .
- the fin 50 is coupled to the plate 32 such that an arc of the fin 50 is arranged along a circumferential direction of the plate 32 .
- peaks on one side of the triangular wave shape are coupled to an outer surface of one of the plates 32 .
- Remaining peaks of the triangular wave shape are coupled to an outer surface of another one of the plates 32 adjacent to the one of the plates 32 .
- the first portions 52 and the second portions 54 are each arranged in a direction orthogonal to the flow direction of the exhaust gas 112 .
- the individual first portions 52 may have the same number of the first openings 56 regardless of locations of the individual first portions 52 in a radial direction, or may have a larger number of the first openings 56 as the first portion 52 is located closer to an outer periphery. Also, it is preferred that the number of the second openings 60 provided to one of the second portions 54 be the same as the number of the first openings 56 provided to the first portion 52 corresponding to the one of the second portions 54 .
- the first opening 56 and the second opening 60 forming at least one of the opening pairs 70 are at least partially non-overlapping, that is, in a non-overlapping positional relationship along the flow direction of the exhaust gas 112 .
- the opening pair 70 herein means a pair of the first opening 56 and the second opening 60 , the second opening 60 satisfying a specified condition, among the first openings 56 and the second openings 60 provided to an individual pair of the first portion 52 and the second portion 54 .
- the specified condition herein may be that the second opening 60 is located nearest to the first opening 56 , or may be another condition.
- the non-overlapping positional relationship in the present embodiment specifically means that the second opening 60 is entirely non-overlapping with the paired first opening 56 in the opening pair 70 in a normal direction of the first portion 52 .
- the non-overlapping positional relationship includes, for example, a relationship in which the second openings 60 and the first openings 56 are arranged zigzag.
- a positional relationship between the first opening 56 and the second opening 60 forming each of the opening pairs 70 is the non-overlapping positional relationship.
- the gap 64 , the first openings 56 , the second openings 60 , and the gap 66 function as the flow path of the exhaust gas 112 .
- Heat exchange is performed between the high-temperature fluid (a second fluid), which is the exhaust gas 112 flowing through the gap 64 , the first openings 56 , the second openings 60 , and the gap 66 , and the low-temperature fluid (a first fluid), which is the coolant 114 flowing through each of the plates 32 . That is, in the present embodiment, the heat exchanging chamber 28 in which the heat exchanger 30 is arranged functions as the heat exchanging portion 6 .
- the retaining member 24 shown in FIG. 2 is a member to retain the heat exchanger 30 arranged in the heat exchanging chamber 28 .
- An introducing member 80 is a cylindrical member having a diameter larger than that of the exhaust pipe 12 and having one end coupled to the retaining member 24 .
- the other end of the introducing member 80 opposite to the one end coupled to the retaining member 24 has a diffuser shape with a gradually increasing diameter.
- the introducing member 80 is arranged to provide an opening between the introducing member 80 and the exhaust pipe 12 .
- the opening functions as an inflow port for the exhaust gas 112 into the heat exchanging portion 6 .
- the valve 10 which comprises at least a valve body 102 and a valve seat 104 , closes the exhaust portion 2 (the introducing member 80 ) by contact of the valve body 102 with the valve seat 104 .
- the diffuser shaped end of the introducing member 80 functions as the valve seat 104 .
- the valve seat 104 of the present disclosure is not limited to this configuration, but a dedicated member may alternatively be provided.
- a mesh member 108 having a meshed configuration is attached to an inner circumferential surface of the valve seat 104 .
- the valve 10 of the present embodiment opens the exhaust portion 2 when a coolant temperature of the coolant 114 in the internal combustion engine 110 is higher than a specified temperature that is previously determined. On the other hand, the valve 10 closes the exhaust portion 2 when the coolant temperature of the coolant 114 in the internal combustion engine 110 is lower than the specified temperature.
- the fins 50 provided to the heat exchanger 30 extend such that the wall surfaces are orthogonal to the flow direction of the exhaust gas 112 .
- the exhaust gas 112 contact the entire wall surfaces of the fins 50 . Accordingly, a large contact area between the fins 50 and the exhaust gas 112 can be ensured, and a more efficient heat transfer from the exhaust gas 112 to the coolant 114 can be achieved.
- the exhaust gas 112 that has passed through the first opening 56 of the fin 50 strikes a region, which faces the first opening 56 , of the second portion 54 .
- the flow of the exhaust gas 112 is disturbed; thus, it is possible to inhibit formation of a boundary layer in the region of the second portion 54 struck by the exhaust gas 112 .
- the heat exchanger 30 enables an efficient heat transfer between the exhaust gas 112 flowing between the plates 32 and the coolant 114 flowing through the plates 32 .
- the first opening 56 and the second opening 60 paired as the at least one opening pair 70 are entirely non-overlapping along the flow direction of the exhaust gas 112 , and also all of the opening pairs 70 are in the non-overlapping positional relationship.
- the heat exchanger 30 enables to increase the area of the second portion 54 to be struck by the exhaust gas 112 that has passed through the first openings 56 . According to the heat exchanger 30 , therefore, formation of a boundary layer can be inhibited in a larger area.
- the heat exchanger 30 enables further improvement in heat exchange rate from the high-temperature fluid to the low-temperature fluid.
- cylindrical plates 32 are stacked in an axial direction in the heat exchanger 30 .
- the fins 50 are arranged so as to have their arcs located along the circumferential direction of the plates 32 .
- the heat exchanger 30 enables to orient the flow direction of the exhaust gas 112 to a direction along the radial direction of the plates 32 .
- the coolant 114 flows along the circumferential direction of the plates 32 .
- the heat exchanger 30 enables to orient the flow direction of the exhaust gas 112 to a direction orthogonal to the flow direction of the coolant 114 .
- the heat exchanger 30 enables to orient the flow direction of the exhaust gas 112 to a direction orthogonal to the flow direction of the coolant 114 in all radial directions of the plates 32 .
- sectional shape of the fin 50 in its entirety is a triangular wave shape in the aforementioned embodiment
- the sectional shape of the fin 50 is not limited to this shape, but may be a sine wave shape, a rectangular wave shape, or a saw-tooth wave shape. That is, the fin 50 may have any sectional shape if the sectional shape of the fin 50 in its entirety is a wave shape.
- the non-overlapping positional relationship is defined that the first opening 56 and the second opening 60 forming the at least one opening pair 70 are entirely non-overlapping along the flow direction of the exhaust gas 112 ; however, the non-overlapping positional relationship is not limited to this relationship, but may be a relationship where the first opening 56 and the second opening 60 forming the at least one opening pair 70 are at least partially non-overlapping.
- all of the opening pairs 70 are each the opening pair 70 having the non-overlapping positional relationship; however, at least one of the opening pairs 70 may be the opening pair 70 having the non-overlapping positional relationship according to the present disclosure.
- the opening between the exhaust downstream end 18 and the introducing member 88 functions as the inflow port for exhaust gas 142 from the exhaust pipe 12 to the heat exchanging portion 6 ; however, the inflow port for exhaust gas 142 from the exhaust pipe 12 to the heat exchanging portion 6 may be holes bored in the exhaust pipe 12 itself.
- the exhaust heat recovery device 1 of the aforementioned embodiment is mounted to a moving body that comprises the internal combustion engine 110 ; however, the exhaust heat recovery device of the present disclosure is not required to be mounted to a moving body. That is, the exhaust heat recovery device in the present disclosure, which is configured to recover heat from the exhaust gas 112 by heat exchange using the exhaust gas 112 from the internal combustion engine 110 as the high-temperature fluid, may be used without being mounted to a moving body. Also, the low-temperature fluid in the exhaust heat recovery device is not limited to the coolant 114 , but may be any other fluid that functions as a low-temperature fluid.
- the heat exchanger 30 is applied to the exhaust heat recovery device 1 in the aforementioned embodiment, the heat exchanger 30 may be applicable to devices other than the exhaust heat recovery device 1 .
- the shape of the heat exchanger 30 is not limited to a cylindrical shape.
- the plates 32 and the fins each may have a rectangular shape or any other shape on condition that the fins 50 coupling the adjacent plates 32 are provided so as to be orthogonal to the flow direction of the second fluid.
Abstract
A heat exchanger in one aspect of the present disclosure comprises a plurality of plates and a fin. The fin comprises at least one first portion and at least one second portion. The at least one first portion is a wall surface that comprises at least one first opening. The at least one second portion, which is paired with the first portion, is a wall surface different from the first portion. The second portion comprises a second opening paired with a corresponding one of the at least one first opening. The fin comprises at least one opening pair, which is a pair of the first opening and the second opening. The at least one opening pair has a non-overlapping positional relationship in which the paired first opening and second opening are at least partially non-overlapping along a flow direction of a second fluid.
Description
- This international application claims the benefit of Japanese Patent Application No. 2014-255334 filed on Dec. 17, 2014 with the Japan Patent Office, and the entire disclosure of Japanese Patent Application No. 2014-255334 is incorporated herein by reference.
- The present disclosure relates to a heat exchanger.
- There has been known an exhaust heat recovery device that is provided with a heat exchanger to exchange heat between exhaust gas from an internal combustion engine as a high-temperature fluid and a low-temperature fluid, and recovers exhaust heat (see
Patent Document 1 below). The heat exchanger described inPatent Document 1 is a stacked plate heat exchanger including a plurality of stacked plates having a flowing space through which the low-temperature fluid flows. The plate of the heat exchanger described inPatent Document 1 includes a convex portion projecting from an outer surface of the plate. - Patent Document 1: International Publication WO2014/014080
- In the heat exchanger described in
Patent Document 1, by providing a convex portion to the outer surface of the plate, a surface area of the outer surface of the plate is increased to thereby improve a heat exchange rate between the low-temperature fluid and the high-temperature fluid. - Generally, heat exchangers are required to achieve improvement in heat exchange rate from a high-temperature fluid to a low-temperature fluid, and a heat exchanger may be desired that achieves a greater heat exchange rate than that of the heat exchanger described in
Patent Document 1. - Accordingly, in one aspect of the present disclosure, it is preferred to provide a heat exchanger allowing an improved heat exchange rate from a high-temperature fluid to a low-temperature fluid.
- One aspect of the present disclosure is a heat exchanger to exchange heat between a first fluid and a second fluid.
- The heat exchanger comprises a plurality of plates and a fin.
- The plurality of plates comprise a flow path through which the first fluid flows. The fin couples mutually adjacent plates among the plurality of plates. Also, the fin comprises at least one first portion and at least one second portion.
- Of these portions, the first portion is a wall surface that comprises at least one first opening. The second portion is a wall surface that is paired with the first portion, and is different from the first portion. The second portion comprises a second opening paired with a corresponding one of the at least one first opening.
- In the fin of the one aspect of the present disclosure, the paired first portion and second portion provide a wave-shaped section. Also, the fin is such that the first portion and the second portion each are arranged in a direction orthogonal to a flow direction of the second fluid. Further, the fin comprises at least one opening pair that is a pair of the first opening and the second opening. The at least one opening pair has a non-overlapping positional relationship in which the paired first opening and second opening are at least partially non-overlapping along the flow direction of the second fluid.
- That is, the fin of the one aspect of the present disclosure extends such that the wall surfaces are orthogonal to the flow direction of the second fluid. Thus, the second fluid contacts the entire wall surfaces of the fin, and a large contact area can be obtained.
- Further, in the one aspect of the present disclosure, the second fluid that has passed through the first opening of the fin strikes an area of the second portion facing the first opening. In the area of the second portion struck by the second fluid, a flow of the second fluid is disturbed; thus, it is possible to inhibit formation of a boundary layer in the area of the second portion struck by the second fluid. Accordingly, the heat exchanger of the one aspect of the present disclosure enables to inhibit formation of the boundary layer between the second fluid and the fin, and enables an efficient heat transfer from the second fluid to the first fluid.
- In other words, the heat exchanger of the one aspect of the present disclosure enables further improvement in heat exchange rate from the high-temperature fluid to the low-temperature fluid.
- The heat exchanger of the one aspect of the present disclosure may be configured as a heat exchanger in which cylindrical plates are stacked in an axial direction. In this case, the fin of one aspect of the present disclosure may be arranged along a circumferential direction of the plates.
- In the aforementioned heat exchanger, the flow direction of the second fluid may be in a direction along a radial direction. Also, in the heat exchanger of the one aspect of the present disclosure, the first fluid flows along the circumferential direction of the plates. Thus, according to the heat exchanger of the one aspect of the present disclosure, the flow direction of the second fluid may be in a direction orthogonal to a flow direction of the first fluid. Further, according to the heat exchanger of the one aspect of the present disclosure, it is achieved that the flow direction of the second fluid is in a direction orthogonal to the flow direction of the first fluid over all radial directions of the plates, that is, over an entire flow area of the second fluid.
- In the at least one opening pair of the heat exchanger of the one aspect of the present disclosure, the paired first opening and second opening may be entirely non-overlapping along the flow direction of the second fluid.
- According to the aforementioned heat exchanger, a large area of the second portion can be struck by the second fluid that has passed through the first opening. Thus, the heat exchanger of the one aspect of the present disclosure enables to inhibit, over a larger area, formation of the boundary layer around a region of the second portion facing the first opening.
- The fin in the heat exchanger of the one aspect of the present disclosure may be such that all the opening pairs each have a non-overlapping positional relationship.
- According to the aforementioned heat exchanger, a much larger area of the second portion can be struck by the second fluid that has passed through the first opening. Thus, the heat exchanger of the one aspect of the present disclosure enables to inhibit, over a much larger area, formation of the boundary layer around a region of the second portion facing the first opening.
-
FIG. 1 is a perspective view showing a schematic outer appearance of an exhaust heat recovery device in an embodiment. -
FIG. 2 is a sectional view of the exhaust heat recovery device in a valve closed condition taken along a line II-II inFIG. 1 . -
FIG. 3 is a side view of a heat exchanger. -
FIG. 4 is a perspective view showing an outer appearance of a plate and a fin. -
FIG. 5 is a perspective view showing an outer appearance of the fin. -
FIG. 6 is a top view of the fin. - 1 . . . exhaust heat recovery device, 2 . . . exhaust portion, 4 . . . shell member, 6 . . . heat exchanging portion, 8 . . . inflow portion, 10 . . . valve, 12, 14 . . . exhaust pipe, 16 . . . upstream end, 18 . . . exhaust downstream end, 20 . . . outer shell member, 22 . . . lid member, 24 . . . retaining member, 28 . . . heat exchanging chamber, 30 . . . heat exchanger, 32 . . . plate, 34 . . . first plate portion, 36 . . . second plate portion, 38 . . . first communicating portion, 39 . . . second communicating portion, 40 . . . first cylindrical portion, 42 . . . second cylindrical portion, 44 . . . inflow pipe, 46 . . . outflow pipe, 50 . . . fin, 52 . . . first portion, 54 . . . second portion, 56 . . . first opening, 58 . . . first opening portion, 60 . . . second opening, 62 . . . second opening portion, 64, 66 . . . gap, 80 . . . introducing member, 102 . . . valve body, 104 . . . valve seat, 108 . . . mesh member, 110 . . . internal combustion engine, 112 . . . exhaust gas (second fluid), 114 . . . coolant (first fluid)
- Hereinafter, an embodiment will be described as one example of the present disclosure with reference to the drawings.
- An exhaust
heat recovery device 1 shown inFIG. 1 is mounted in a moving body that comprises aninternal combustion engine 110. The exhaustheat recovery device 1 exchanges heat betweenexhaust gas 112 from theinternal combustion engine 110 as a high-temperature fluid and acoolant 114 of theinternal combustion engine 110 as a low-temperature fluid, to thereby recover heat from theexhaust gas 112. Theexhaust gas 112 of the present embodiment is one example of “a second fluid” of the present disclosure, and thecoolant 114 is one example of “a first fluid” of the present disclosure. Thecoolant 114 of the present embodiment may be cooling water or may be oil. - The exhaust
heat recovery device 1 of the present embodiment comprises anexhaust portion 2, ashell member 4, a heat exchanging portion 6 (seeFIG. 2 ), an inflow portion 8 (seeFIG. 2 ), and avalve 10. - The
exhaust portion 2 comprises a path to guideexhaust gas 112 from theinternal combustion engine 110 toward downstream. Theshell member 4 is a member covering an outside of theexhaust portion 2. - The heat exchanging portion 6 comprises a heat exchanger 30 (see
FIG. 2 ) arranged between theexhaust portion 2 and theshell member 4, and performs heat exchange between theexhaust gas 112 as the high-temperature fluid and the low-temperature fluid that flows insideplates 32 of theheat exchanger 30. - The inflow portion 8 is a portion through which the
exhaust gas 112 flows from theexhaust portion 2 into the heat exchanging portion 6. Thevalve 10, which is a known valve that opens and closes a path, is arranged downstream from the inflow portion 8 along a flow path of theexhaust gas 112 in theexhaust portion 2. - Next, a description will be given of a configuration of the exhaust
heat recovery device 1. - As shown in
FIG. 2 , theexhaust portion 2 comprises anexhaust pipe 12. - The
exhaust pipe 12 is a cylindrical member. Theexhaust gas 112 from theinternal combustion engine 110 flows into theexhaust pipe 12. - The
shell member 4 comprises anexhaust pipe 14, anouter shell member 20, alid member 22, and a retainingmember 24. - The
exhaust pipe 14 is a generally cylindrical member comprising anupstream end 16 as one end having an opening with an inner diameter greater than an outer diameter of theexhaust pipe 12. In an internal space of theexhaust pipe 14 at theupstream end 16, an exhaustdownstream end 18, which is an end opposite to an upstream end, of theexhaust pipe 12 is arranged in a non-contact state with theshell member 4. - The
outer shell member 20 is a cylindrical member with an inner diameter greater than a diameter of theexhaust pipe 12. - A downstream end of the
outer shell member 20 is coupled to theupstream end 16 of theexhaust pipe 14. - The
lid member 22 closes an upstream opening of theouter shell member 20 along the flow path of theexhaust gas 112 in theexhaust pipe 12. - In other words, the
outer shell member 20, thelid member 22, and theexhaust pipe 12 provide aheat exchanging chamber 28 that is an annular space surrounded by theouter shell member 20, thelid member 22, and theexhaust pipe 12. - The
heat exchanger 30 arranged in theheat exchanging chamber 28 is a heat exchanger, in which thecoolant 114 flows and which is arranged so as to cover an outer circumference of theexhaust pipe 12. - As shown in
FIG. 3 , theheat exchanger 30 of the present embodiment comprises a plurality of plates 32-1 to 32-N, aninflow pipe 44, anoutflow pipe 46, and a plurality of fins 50-1 to 50-M. That is, theheat exchanger 30 is a so-called stacked-plate heat exchanger. - Here, a symbol N, which is an identifier denoting the number of the
plates 32, is a positive integer of 2 or more. Also, a symbol M in the present embodiment is an identifier denoting the number of thefins 50. The symbol M is, for example, a positive integer smaller by “1” than N. - Each of the
plates 32 comprises a flow path through which thecoolant 114 flows. Thefin 50 couples mutuallyadjacent plates 32 among the plurality ofplates 32. Theinflow pipe 44 is a pipe to cause thecoolant 114 from outside theheat exchanger 30 to flow into oneplate 32. Theoutflow pipe 46 is a pipe to cause thecoolant 114 to flow out of theheat exchanger 30 from oneplate 32. - As shown in
FIG. 4 , each of theplates 32 comprises afirst plate portion 34 and asecond plate portion 36. - The
first plate portion 34 is a ring-shaped member. Thefirst plate portion 34 comprises a wall portion protruding in a same direction from a periphery of thefirst plate portion 34. Thesecond plate portion 36 is a ring-shaped member. Thesecond plate portion 36 comprises a wall portion protruding in a same direction from a periphery of thesecond plate portion 36. - Each of the
plates 32 is formed by engaging the wall portion of thefirst plate portion 34 with the wall portion of thesecond plate portion 36. Each of theplates 32 comprises a gap between an inner surface of thefirst plate portion 34 and an inner surface of thesecond plate portion 36. The gap functions as a flowing space in which the low-temperature fluid flows, that is, a flow path of thecoolant 114. - Each of the
plates 32 comprises a first communicatingportion 38 and a second communicatingportion 39. Of these communicating portions, the first communicatingportion 38 comprises a flow path through which thecoolant 114 from theinflow pipe 44 flows into anadjacent plate 32 from upstream toward downstream along the flow path of theexhaust gas 112 in theexhaust portion 2. The second communicatingportion 39 comprises a flow path through which thecoolant 114 flows into anadjacent plate 32 from downstream to theoutflow pipe 46 along the flow path of theexhaust gas 112 in theexhaust portion 2. - Each of the first communicating
portion 38 and the second communicatingportion 39 of the present embodiment comprises a firstcylindrical portion 40 and a secondcylindrical portion 42. The firstcylindrical portion 40 is a cylindrical portion that is erected from an opening provided to thefirst plate portion 34 in a direction opposite to that of the wall portion. The secondcylindrical portion 42 is a cylindrical portion that is erected from a periphery of an opening provided to thesecond plate portion 36 in a direction opposite to that of the wall portion. - When joined, the first
cylindrical portions 40 provided to thefirst plate portion 34 and the secondcylindrical portions 42 provided to thesecond plate portion 36 function as the first communicatingportion 38 and the second communicatingportion 39. The secondcylindrical portion 42 provided to thesecond plate portion 36 here means the secondcylindrical portion 42 provided to thesecond plate portion 36 that is adjacent to an outer surface of thefirst plate portion 34 through thefin 50. - A configuration method of the first communicating
portion 38 and the second communicatingportion 39 is not limited to this, and any configuration may be employed in which these portions are configured to function as a flow path for thecoolant 114 through theplates 32. - Each of the
plates 32 is also arranged so as to cover the outer circumference of theexhaust pipe 12. Each of theplates 32 is arranged so as to have agap 64 between a center side periphery of theplate 32 in a radial direction thereof and an outer surface of theexhaust pipe 12, thegap 64 being located along a radial direction of theexhaust pipe 12. Also, each of theplates 32 is arranged so as to have agap 66 between an outer side periphery of theplate 32 in the radial direction thereof and an inner surface of theouter shell member 20, thegap 66 being located along the radial direction of theexhaust pipe 12. - With this configuration, the
exhaust gas 112 in the present embodiment flows in a direction from the outer surface of theexhaust pipe 12 toward the inner surface of theouter shell member 20 along a radial direction of theplate 32. - The
fin 50 is a truncated arc member coupled to twoplates 32 adjacent to each other. As shown inFIG. 5 andFIG. 6 , thefin 50 comprises first portions 52-1 to 52-L and second portions 54-1 to 54-L. In thefin 50, thefirst portions 52 and thesecond portions 54 are coupled, to thereby provide a triangular wave-shaped section of thefin 50 in its entirety. A symbol “L” here is an integer of 1 or more. - The
first portions 52 are each a rectangular plate portion that functions as a wall surface of thefin 50. Thefirst portions 52 each comprise at least onefirst opening portion 58 having afirst opening 56. In the present embodiment, thefirst portions 52 each may have thefirst openings 56 arranged at equal intervals, or may have thefirst openings 56 arranged at unequal intervals. - The
second portions 54 are each a rectangular plate portion that is paired with thefirst portion 52 and functions as a wall surface different from thefirst portion 52. Also, thesecond portions 54 each comprise at least onesecond opening portion 62 having asecond opening 60 that is paired with thefirst opening 56. In the present embodiment, the second portions each may have thesecond openings 60 arranged at equal intervals, or may have thesecond openings 60 arranged at unequal intervals. - Areas of the individual
first openings 56, areas of the individualsecond openings 60, a total area of thefirst openings 56, and a total area of thesecond openings 60 may be appropriately determined in consideration of a pressure of theexhaust gas 112. - One side in a longitudinal direction of one of the
first portions 52 is coupled to one side in a longitudinal direction of one of thesecond portions 54. The other side in the longitudinal direction of the one of thefirst portions 52 is coupled to one side in a longitudinal direction of a different one of thesecond portions 54. With the aforementioned configuration, the triangular wave-shaped section of thefin 50 in its entirety is provided. - Further, the
fin 50 is coupled to theplate 32 such that an arc of thefin 50 is arranged along a circumferential direction of theplate 32. Specifically, in thefin 50, peaks on one side of the triangular wave shape are coupled to an outer surface of one of theplates 32. Remaining peaks of the triangular wave shape are coupled to an outer surface of another one of theplates 32 adjacent to the one of theplates 32. With this configuration, in the present embodiment, thefirst portions 52 and thesecond portions 54 are each arranged in a direction orthogonal to the flow direction of theexhaust gas 112. - The individual
first portions 52 may have the same number of thefirst openings 56 regardless of locations of the individualfirst portions 52 in a radial direction, or may have a larger number of thefirst openings 56 as thefirst portion 52 is located closer to an outer periphery. Also, it is preferred that the number of thesecond openings 60 provided to one of thesecond portions 54 be the same as the number of thefirst openings 56 provided to thefirst portion 52 corresponding to the one of thesecond portions 54. - In the
fin 50, among opening pairs 70, each of which is a pair of thefirst opening 56 and thesecond opening 60, thefirst opening 56 and thesecond opening 60 forming at least one of the opening pairs 70 are at least partially non-overlapping, that is, in a non-overlapping positional relationship along the flow direction of theexhaust gas 112. - The opening pair 70 herein means a pair of the
first opening 56 and thesecond opening 60, thesecond opening 60 satisfying a specified condition, among thefirst openings 56 and thesecond openings 60 provided to an individual pair of thefirst portion 52 and thesecond portion 54. The specified condition herein may be that thesecond opening 60 is located nearest to thefirst opening 56, or may be another condition. - The non-overlapping positional relationship in the present embodiment specifically means that the
second opening 60 is entirely non-overlapping with the paired first opening 56 in the opening pair 70 in a normal direction of thefirst portion 52. The non-overlapping positional relationship includes, for example, a relationship in which thesecond openings 60 and thefirst openings 56 are arranged zigzag. In the present embodiment, a positional relationship between thefirst opening 56 and thesecond opening 60 forming each of the opening pairs 70 is the non-overlapping positional relationship. - In the present embodiment, the
gap 64, thefirst openings 56, thesecond openings 60, and thegap 66 function as the flow path of theexhaust gas 112. - Heat exchange is performed between the high-temperature fluid (a second fluid), which is the
exhaust gas 112 flowing through thegap 64, thefirst openings 56, thesecond openings 60, and thegap 66, and the low-temperature fluid (a first fluid), which is thecoolant 114 flowing through each of theplates 32. That is, in the present embodiment, theheat exchanging chamber 28 in which theheat exchanger 30 is arranged functions as the heat exchanging portion 6. - The retaining
member 24 shown inFIG. 2 is a member to retain theheat exchanger 30 arranged in theheat exchanging chamber 28. - An introducing
member 80 is a cylindrical member having a diameter larger than that of theexhaust pipe 12 and having one end coupled to the retainingmember 24. The other end of the introducingmember 80 opposite to the one end coupled to the retainingmember 24 has a diffuser shape with a gradually increasing diameter. - The introducing
member 80 is arranged to provide an opening between the introducingmember 80 and theexhaust pipe 12. The opening functions as an inflow port for theexhaust gas 112 into the heat exchanging portion 6. - The
valve 10, which comprises at least avalve body 102 and avalve seat 104, closes the exhaust portion 2 (the introducing member 80) by contact of thevalve body 102 with thevalve seat 104. In the present embodiment, the diffuser shaped end of the introducingmember 80 functions as thevalve seat 104. Thevalve seat 104 of the present disclosure, however, is not limited to this configuration, but a dedicated member may alternatively be provided. - A
mesh member 108 having a meshed configuration is attached to an inner circumferential surface of thevalve seat 104. - The
valve 10 of the present embodiment opens theexhaust portion 2 when a coolant temperature of thecoolant 114 in theinternal combustion engine 110 is higher than a specified temperature that is previously determined. On the other hand, thevalve 10 closes theexhaust portion 2 when the coolant temperature of thecoolant 114 in theinternal combustion engine 110 is lower than the specified temperature. - When the
valve 10 is closed to thereby close theexhaust portion 2 in the exhaustheat recovery device 1, theexhaust gas 112 from theinternal combustion engine 110 flows through the inflow portion 8 into the heat exchanging portion 6, and heat exchange with thecoolant 114 is performed in the heat exchanging portion 6. - The
fins 50 provided to theheat exchanger 30 extend such that the wall surfaces are orthogonal to the flow direction of theexhaust gas 112. Thus, theexhaust gas 112 contact the entire wall surfaces of thefins 50. Accordingly, a large contact area between thefins 50 and theexhaust gas 112 can be ensured, and a more efficient heat transfer from theexhaust gas 112 to thecoolant 114 can be achieved. - Also, the
exhaust gas 112 that has passed through thefirst opening 56 of thefin 50 strikes a region, which faces thefirst opening 56, of thesecond portion 54. In the area of thesecond portion 54 struck by theexhaust gas 112, the flow of theexhaust gas 112 is disturbed; thus, it is possible to inhibit formation of a boundary layer in the region of thesecond portion 54 struck by theexhaust gas 112. Accordingly, theheat exchanger 30 enables an efficient heat transfer between theexhaust gas 112 flowing between theplates 32 and thecoolant 114 flowing through theplates 32. - Particularly, in the present embodiment, the
first opening 56 and thesecond opening 60 paired as the at least one opening pair 70 are entirely non-overlapping along the flow direction of theexhaust gas 112, and also all of the opening pairs 70 are in the non-overlapping positional relationship. - Thus, the
heat exchanger 30 enables to increase the area of thesecond portion 54 to be struck by theexhaust gas 112 that has passed through thefirst openings 56. According to theheat exchanger 30, therefore, formation of a boundary layer can be inhibited in a larger area. - As described above, the
heat exchanger 30 enables further improvement in heat exchange rate from the high-temperature fluid to the low-temperature fluid. - Also, the
cylindrical plates 32 are stacked in an axial direction in theheat exchanger 30. Thefins 50 are arranged so as to have their arcs located along the circumferential direction of theplates 32. - Accordingly, the
heat exchanger 30 enables to orient the flow direction of theexhaust gas 112 to a direction along the radial direction of theplates 32. Also, in theheat exchanger 30 with this configuration, thecoolant 114 flows along the circumferential direction of theplates 32. Thus, theheat exchanger 30 enables to orient the flow direction of theexhaust gas 112 to a direction orthogonal to the flow direction of thecoolant 114. Further, theheat exchanger 30 enables to orient the flow direction of theexhaust gas 112 to a direction orthogonal to the flow direction of thecoolant 114 in all radial directions of theplates 32. - Although the embodiment of the present disclosure has been described above, the present disclosure is not limited to the aforementioned embodiment, but may be practiced in various forms within the scope not departing from the spirit of the present disclosure.
- For example, although the sectional shape of the
fin 50 in its entirety is a triangular wave shape in the aforementioned embodiment, the sectional shape of thefin 50 is not limited to this shape, but may be a sine wave shape, a rectangular wave shape, or a saw-tooth wave shape. That is, thefin 50 may have any sectional shape if the sectional shape of thefin 50 in its entirety is a wave shape. - Also, in the aforementioned embodiment, the non-overlapping positional relationship is defined that the
first opening 56 and thesecond opening 60 forming the at least one opening pair 70 are entirely non-overlapping along the flow direction of theexhaust gas 112; however, the non-overlapping positional relationship is not limited to this relationship, but may be a relationship where thefirst opening 56 and thesecond opening 60 forming the at least one opening pair 70 are at least partially non-overlapping. - Further, in the aforementioned embodiment, all of the opening pairs 70 are each the opening pair 70 having the non-overlapping positional relationship; however, at least one of the opening pairs 70 may be the opening pair 70 having the non-overlapping positional relationship according to the present disclosure.
- In the aforementioned embodiment, the opening between the exhaust
downstream end 18 and the introducing member 88 functions as the inflow port for exhaust gas 142 from theexhaust pipe 12 to the heat exchanging portion 6; however, the inflow port for exhaust gas 142 from theexhaust pipe 12 to the heat exchanging portion 6 may be holes bored in theexhaust pipe 12 itself. - Moreover, the exhaust
heat recovery device 1 of the aforementioned embodiment is mounted to a moving body that comprises theinternal combustion engine 110; however, the exhaust heat recovery device of the present disclosure is not required to be mounted to a moving body. That is, the exhaust heat recovery device in the present disclosure, which is configured to recover heat from theexhaust gas 112 by heat exchange using theexhaust gas 112 from theinternal combustion engine 110 as the high-temperature fluid, may be used without being mounted to a moving body. Also, the low-temperature fluid in the exhaust heat recovery device is not limited to thecoolant 114, but may be any other fluid that functions as a low-temperature fluid. - Although the
heat exchanger 30 is applied to the exhaustheat recovery device 1 in the aforementioned embodiment, theheat exchanger 30 may be applicable to devices other than the exhaustheat recovery device 1. - Also, the shape of the
heat exchanger 30 is not limited to a cylindrical shape. Specifically, in the heat exchanger of the present disclosure, theplates 32 and the fins each may have a rectangular shape or any other shape on condition that thefins 50 coupling theadjacent plates 32 are provided so as to be orthogonal to the flow direction of the second fluid. - Any form in which part of a configuration in the aforementioned embodiment is omitted may be an embodiment of the present disclosure. Also, any form in which the aforementioned embodiment and a modified example are appropriately combined may be an embodiment of the present disclosure. Further, any form that can be conceived within the scope not departing from the essence of the present disclosure defined by the language of the claims may be an embodiment of the present disclosure.
Claims (7)
1. A heat exchanger to exchange heat between a first fluid and a second fluid, the heat exchanger comprising:
a plurality of plates comprising a flow path through which the first fluid flows; and
a fin configured to couple mutually adjacent plates among the plurality of plates,
wherein the fin comprises:
at least one first portion that is a wall surface and comprises at least one first opening;
at least one second portion that is a wall surface paired with the first portion and is different from the first portion, the at least one second portion comprising a second opening paired with a corresponding one of the at least one first opening,
the paired first portion and second portion providing a wave-shaped section, and
the first portion and the second portion each being arranged in a direction orthogonal to a flow direction of the second fluid; and
at least one opening pair that is a pair of the first opening and the second opening,
the at least one opening pair having a non-overlapping positional relationship in which the paired first opening and second opening are at least partially non-overlapping along the flow direction of the second fluid.
2. The heat exchanger according to claim 1 ,
wherein each of the plurality of plates has a cylindrical shape,
wherein the plurality of plates are arranged along an axial direction, and
wherein the fin is arranged along a circumferential direction of the plates.
3. The heat exchanger according to claim 1 , wherein the at least one opening pair is such that the paired first opening and second opening are entirely non-overlapping along the flow direction of the second fluid.
4. The heat exchanger according to claim 1 , wherein the fin is such that each of the opening pair has the non-overlapping positional relationship.
5. The heat exchanger according to claim 2 , wherein the at least one opening pair is such that the paired first opening and second opening are entirely non-overlapping along the flow direction of the second fluid.
6. The heat exchanger according to claim 2 , wherein the fin is such that each of the opening pair has the non-overlapping positional relationship.
7. The heat exchanger according to claim 3 , wherein the fin is such that each of the opening pair has the non-overlapping positional relationship.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2014-255334 | 2014-12-17 | ||
JP2014255334A JP2016114331A (en) | 2014-12-17 | 2014-12-17 | Heat exchanger |
PCT/JP2015/083261 WO2016098555A1 (en) | 2014-12-17 | 2015-11-26 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
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US20170343302A1 true US20170343302A1 (en) | 2017-11-30 |
Family
ID=56126452
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US15/535,793 Abandoned US20170343302A1 (en) | 2014-12-17 | 2015-11-26 | Heat exchanger |
Country Status (5)
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US (1) | US20170343302A1 (en) |
JP (1) | JP2016114331A (en) |
CN (1) | CN107003084A (en) |
DE (1) | DE112015005686T5 (en) |
WO (1) | WO2016098555A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10641557B2 (en) * | 2017-12-29 | 2020-05-05 | Cooler Master Co., Ltd. | Combined heat sink |
US11448465B2 (en) * | 2019-03-26 | 2022-09-20 | Ngk Insulators, Ltd. | Heat exchanger |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150226496A1 (en) * | 2012-09-26 | 2015-08-13 | Hangzhou Sanhua Research Institute Co., Ltd. | Fin of heat exchanger and heat exchanger |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5030145A (en) * | 1973-07-19 | 1975-03-26 | ||
CN1051844C (en) * | 1993-08-28 | 2000-04-26 | 梅兰尼西亚国际信托有限公司 | Improved heat exchanger element |
US7278472B2 (en) * | 2002-09-20 | 2007-10-09 | Modine Manufacturing Company | Internally mounted radial flow intercooler for a combustion air changer |
JP2014095482A (en) * | 2012-11-07 | 2014-05-22 | Keihin Thermal Technology Corp | Double-pipe heat exchanger |
JP2014194319A (en) * | 2013-03-29 | 2014-10-09 | Calsonic Kansei Corp | Heat exchanger |
-
2014
- 2014-12-17 JP JP2014255334A patent/JP2016114331A/en active Pending
-
2015
- 2015-11-26 WO PCT/JP2015/083261 patent/WO2016098555A1/en active Application Filing
- 2015-11-26 DE DE112015005686.6T patent/DE112015005686T5/en not_active Withdrawn
- 2015-11-26 US US15/535,793 patent/US20170343302A1/en not_active Abandoned
- 2015-11-26 CN CN201580068775.5A patent/CN107003084A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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US20150226496A1 (en) * | 2012-09-26 | 2015-08-13 | Hangzhou Sanhua Research Institute Co., Ltd. | Fin of heat exchanger and heat exchanger |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10641557B2 (en) * | 2017-12-29 | 2020-05-05 | Cooler Master Co., Ltd. | Combined heat sink |
US11448465B2 (en) * | 2019-03-26 | 2022-09-20 | Ngk Insulators, Ltd. | Heat exchanger |
Also Published As
Publication number | Publication date |
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DE112015005686T5 (en) | 2017-09-07 |
CN107003084A (en) | 2017-08-01 |
JP2016114331A (en) | 2016-06-23 |
WO2016098555A1 (en) | 2016-06-23 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |