EP4365535A1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP4365535A1
EP4365535A1 EP22864582.6A EP22864582A EP4365535A1 EP 4365535 A1 EP4365535 A1 EP 4365535A1 EP 22864582 A EP22864582 A EP 22864582A EP 4365535 A1 EP4365535 A1 EP 4365535A1
Authority
EP
European Patent Office
Prior art keywords
offset
fin
flowing direction
plate joint
joint part
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.)
Pending
Application number
EP22864582.6A
Other languages
English (en)
French (fr)
Inventor
Shunsaku EGUCHI
Yoichi Uefuji
Gento ICHIKAWA
Masayoshi Hirasawa
Katsuhiro Saito
Hiroyuki NAKAHARAI
Yuta Takahashi
Takafumi Kamei
Takeshi Kaneko
Koichi Tanimoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP4365535A1 publication Critical patent/EP4365535A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • 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
    • 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
    • F28D9/0062—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 spaced plates with inserted elements
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present disclosure relates to a heat exchanger.
  • a heat exchanger such as an oil cooler using offset fins as inner fins is known (for example, refer to PTL 1).
  • This oil cooler includes a tube through which oil circulates inside and a cooling medium circulates outside, and offset fins that are arranged inside the tube to perform heat exchange between the oil and the cooling medium.
  • the offset fins have a wavy cross-sectional shape perpendicular to a flowing direction of the oil in which convex portions are alternately positioned on one side and the other side.
  • a thermal boundary layer is formed on a fin wall surface between the fluids passing on both sides of the offset fins, where a high-temperature fluid such as oil and a low-temperature fluid such as a cooling medium exchange heat.
  • the thermal boundary layer is a layer formed by a temperature gradient that occurs between the fluid heated or cooled at the fin wall surface and the fluid near the wall surface. The thickness of the thermal boundary layer increases due to heat exchange, and in a case where the temperature gradient in the fluid near the wall surface decreases, heat exchange is suppressed and heat transfer performance decreases, resulting in a decrease in heat exchange performance of the heat exchanger.
  • an object of the present disclosure is to provide a heat exchanger that can suppress a decrease in heat transfer performance by reducing a thickness of a thermal boundary layer.
  • a heat exchanger includes a pair of plates that face each other; and an inner fin which is provided between the pair of plates and in which a fluid circulates, in which the inner fin has a plurality of offset fins which are arranged side by side in a flowing direction of the fluid and are provided such that positions thereof are mutually offset in a width direction perpendicular to the flowing direction, and the offset fin includes a plate joint part which is joined to the plate and has a step formed in the flowing direction, a fin part which is provided along an opposing direction of the pair of plates and is connected to the plate joint part, and a reception slope which is provided to the plate joint part, obliquely to the flowing direction, and which receives the fluid from the step.
  • a heat exchanger includes a pair of plates that face each other; and an inner fin which is provided between the pair of plates and in which a fluid circulates, in which the inner fin has a plurality of offset fins which are arranged side by side in a flowing direction of the fluid and are provided such that positions thereof are mutually offset in a width direction perpendicular to the flowing direction, and the offset fin includes a plate joint part which is joined to the plate, a fin part which is provided along an opposing direction of the pair of plates and is connected to the plate joint part, and a protrusion portion which is provided on the plate joint part and protrudes inward from the plate joint part.
  • a heat exchanger includes a pair of plates that face each other; and an inner fin which is provided between the pair of plates and in which a fluid circulates, in which the inner fin has a plurality of offset fins which are arranged side by side in a flowing direction of the fluid and are provided such that positions thereof are mutually offset in a width direction perpendicular to the flowing direction, and the offset fin includes a plate joint part which is joined to the plate, a fin part which is provided along an opposing direction of the pair of plates and is connected to the plate joint part, and a hole that is provided to the plate joint part and is recessed from the plate joint part toward the plate.
  • a decrease in heat transfer performance can be suppressed by suppressing formation of a thermal boundary layer.
  • a heat exchanger 1 is a heat exchanger having a stacked structure in which inner fins are provided between a pair of plates, and is a so-called plate heat exchanger.
  • heat exchange is performed between a high-temperature fluid and a low-temperature fluid that circulates inside the heat exchanger 1.
  • the fluid circulating inside the heat exchanger 1 may be a liquid or a gas, and is not particularly limited.
  • Fig. 1 is a perspective view schematically illustrating the heat exchanger according to the first embodiment.
  • Fig. 2 is a perspective view illustrating the offset fin of the heat exchanger according to the first embodiment.
  • Fig. 3 is a two-sided view of the offset fin.
  • Fig. 4 is a sectional view of the offset fin.
  • Fig. 5 is an explanatory diagram regarding a flow of the fluid.
  • the heat exchanger 1 includes a plurality of plates 10 and inner fins 12 provided between the plates 10.
  • the plate 10 is formed in a plate shape.
  • the plurality of plates 10 are arranged at predetermined intervals in an opposing direction in which plate surfaces of the plates 10 face each other, that is, in a thickness direction.
  • a high-temperature fluid circulates through one side in the thickness direction, and a low-temperature fluid circulates through the other side in the thickness direction.
  • the plate 10 is made of a metallic material with high heat transfer performance.
  • the inner fins 12 are provided between a pair of plates 10 that are adjacent to each other, and are joined to the plates 10 by brazing. That is, one side of the inner fins 12 in the thickness direction is joined to the plate 10 on one side, and the other side of the inner fins 12 in the thickness direction is joined to the plate on the other side.
  • the inner fins 12 function as a strength member that supports the pair of plates 10.
  • the inner fins 12 are provided with a flow path through which the fluid circulates. Therefore, the fluid circulates between the pair of plates 10 that face each other, that is, inside the inner fins 12.
  • the plurality of plates 10 and the inner fins 12 are alternately arranged and joined in the thickness direction. Therefore, the flow paths formed by the inner fins 12 are partitioned by the plates 10, so that a plurality of flow paths are arranged in the thickness direction.
  • the plurality of flow paths arranged in the thickness direction allow the high-temperature fluid and the low-temperature fluid to circulate such that the flow path through which the high-temperature fluid circulates and the flow path through which the low-temperature fluid circulates alternate.
  • the flow path is formed such that the fluid flows in one direction in a plane perpendicular to the thickness direction.
  • the flowing direction of the high-temperature fluid and the flowing direction of the low-temperature fluid are opposite directions.
  • the high-temperature fluid in a case where the high-temperature fluid and the low-temperature fluid are made to circulate, the high-temperature fluid circulates in a predetermined flowing direction, and the low-temperature fluid circulates in a flowing direction opposite to the flowing direction of the high-temperature fluid. Then, heat is exchanged between the high-temperature fluid and the low-temperature fluid via the plates 10 and the inner fins 12.
  • the inner fin 12 has a plurality of offset fins 15.
  • the plurality of offset fins 15 are arranged side by side along the flowing direction of the fluid.
  • the plurality of offset fins 15 are provided in a plane perpendicular to the thickness direction such that the positions thereof are mutually offset in the width direction perpendicular to the flowing direction.
  • the offset fins 15 are provided across the width direction.
  • the offset fin 15 has a wavy shape in which a part that protrudes toward an upstream side in the flowing direction is set as a top portion 15a, a part that is depressed toward a downstream side in the flowing direction is set as a valley portion 15b, and the top portion 15a and the valley portion 15b are alternately provided along the width direction.
  • One of the offset fins 15 adjacent to each other in the flowing direction and the other of the offset fins 15 adjacent to each other in the flowing direction are arranged line-symmetrically with the width direction as an axis of symmetry, and are arranged such that the positions thereof are mutually offset in the width direction.
  • an angle ⁇ a at the top portion 15a and the valley portion 15b is in a range from 60 degrees to 160 degrees.
  • the offset fins 15 are arranged in four rows in the flowing direction as one set.
  • the offset fin 15 in the first row that is on the upstream side in the flowing direction and the offset fin 15 in the third row that is on the downstream side in the flowing direction are at the same position in the width direction.
  • the offset fins 15 in the second row is offset to one side in the width direction (to the right in Figs. 3 and 4 ) with respect to the offset fins 15 in the first and third rows.
  • the offset fins 15 in the fourth row is offset to the other side in the width direction (to the left in Figs. 3 and 4 ) with respect to the offset fins 15 in the first and third rows.
  • the distance between the top portions in the width direction is set as one unit.
  • the offset fin 15 in the second row is offset by 1/2 unit to one side in the width direction with respect to the offset fins 15 in the first and third rows.
  • the offset fin 15 in the fourth row is offset by 1/2 unit to the other side in the width direction with respect to the offset fins 15 in the first and third rows.
  • the offset fins 15 in the second and fourth rows are offset by 1/2 unit, but unless restricted by the shape of the offset fins 15, it is preferable to offset the offset fins 15 in the second and fourth rows within a range of 1/4 unit to 1/2 unit.
  • the offset fin 15 has a plate joint part 21, a fin part 22, and an inhibiting part 23, and these parts are integrated.
  • the plate joint part 21 is a part that is joined to the plate 10.
  • the plate joint part 21 includes a plate joint part 21a joined to one side of the pair of plates 10, and a plate joint part 21b joined to the other side of the pair of plates 10.
  • the plate joint part 21 is formed in a parallelogram plate shape or in a V-shaped plate shape obtained by developing a parallelogram symmetrically in the width direction.
  • the plate joint part 21 constitutes a portion of the top portion 15a and the valley portion 15b of the offset fin 15.
  • a surface facing the plate 10 is joined to the plate 10, so that an end portion in the flowing direction, which is exposed on the internal flow path side, is formed as a step 25.
  • the fin part 22 is provided across the thickness direction.
  • the fin part 22 is connected to the end portion of the plate joint part 21 in the width direction.
  • the fin part 22 is formed in a plate shape.
  • the inhibiting part 23 is provided on the plate joint part 21.
  • the inhibiting part 23 is a part that inhibits the formation of the thermal boundary layer that occurs in the fluid circulating along the inside of the plate joint part 21.
  • the inhibiting part 23 is a reception slope 38 that is oblique to the flowing direction and that receives the fluid from the step 25. Since the reception slope 38 is oblique to the flowing direction of the fluid, the fluid flowing along the reception slope 38 becomes a swirling flow that swirls in a circumferential direction with the flowing direction as an axis.
  • FIG. 5 illustrates a section taken along a plane perpendicular to the flowing direction, with an upper side of the figure being the upstream side in the flowing direction, and a lower side of the figure being the downstream side in the flowing direction.
  • a flow R1 from the top portion 15a toward the valley portion 15b in the width direction is generated.
  • the fluid becomes a swirling flow R2 that swirls in the flowing direction from the top portion 15a to the valley portion 15b. Since the flow velocity of the fluid as the swirling flow R2 increases on the inner side of the plate joint part 21, the formation of the thermal boundary layer occurring on the inner side of the plate joint part 21 is inhibited.
  • Fig. 6 is a perspective view illustrating an offset fin of a heat exchanger according to a second embodiment.
  • Fig. 7 is a perspective view illustrating a protrusion portion of the offset fin.
  • Fig. 8 is a two-sided view of the offset fin.
  • a plurality of offset fins 51 in the inner fins 12 are different from the offset fins 15 of the first embodiment.
  • the plurality of offset fins 51 are arranged side by side along the flowing direction of the fluid.
  • the plurality of offset fins 51 are provided in a plane perpendicular to the thickness direction such that the positions thereof are mutually offset in the width direction perpendicular to the flowing direction.
  • the offset fins 51 are provided across the width direction. That is, the offset fin 15 is an elongated member of which a longitudinal direction is the width direction. As illustrated in Figs. 6 and 8 , the offset fin 51 has a plate joint part 61, a fin part 62, and an inhibiting part 63, and these parts are integrated.
  • the plate joint part 61 is a part that is joined to the plate 10. Similar to the plate joint part 21 of the first embodiment, the plate joint part 61 includes a plate joint part 61a joined to one side of the pair of plates 10, and a plate joint part 61b joined to the other side of the pair of plates 10. The plate joint part 61 is formed into a rectangular plate shape. In addition, in the plate joint part 61, a surface facing the plate 10 is joined to the plate 10, so that an end portion in the flowing direction, which is exposed on the internal flow path side, is formed as the step 25.
  • the fin part 62 is provided across the thickness direction.
  • the fin part 62 is connected to the end portion of the plate joint part 61 in the width direction.
  • the fin part 62 is formed in a plate shape.
  • the inhibiting part 63 is provided on the plate joint part 61. Similar to the first embodiment, the inhibiting part 63 is a part that inhibits the formation of the thermal boundary layer that occurs in the fluid circulating along the inside of the plate joint part 61. Specifically, the inhibiting part 63 is a protrusion portion 65 that protrudes inward from the plate joint part 61. In a case where the plate joint parts 61 are continuous in the offset fins 51 adjacent to each other in the flowing direction, the protrusion portion 65 is provided on the plate joint part 61 on the upstream side in the flowing direction.
  • the protrusion portion 65 is formed in a rectangular shape that is long in the flowing direction in plan view seen from the height direction perpendicular to the flowing direction and to the width direction.
  • the protrusion portion 65 is formed in a triangular shape convex in a protrusion direction in front view seen from the flowing direction.
  • the protrusion portion 65 has a rectangular shape in plan view and a triangular shape in front view, but is not particularly limited to this shape.
  • the protrusion portion 65 may have a polygonal shape or an annular shape such as a circle or an ellipse in plan view, and may have a polygonal shape or an arcuate shape such as a semicircle or an ellipse in front view.
  • the protrusion portion 65 has a first guide slope 65a that slopes from the upstream side toward the downstream side in the flowing direction, and a second guide slope 65b that slopes from one side toward the other side in the width direction.
  • the first guide slope 65a includes an upstream-side guide slope 65a and a downstream-side guide slope 65a. Assuming that an angle formed by the first guide slope 65a and the flowing direction is a first inclination angle ⁇ 1, the first inclination angle ⁇ 1 is in a range of 10 degrees to 60 degrees.
  • the first inclination angle ⁇ 1 on the downstream side may be the same as the first inclination angle ⁇ 1 on the upstream side, or may be larger than the first inclination angle ⁇ 1 on the upstream side with an upper limit of 90 degrees.
  • the second guide slope 65b includes a guide slope 65b on one side in the width direction and a guide slope 65b on the other side in the width direction. Assuming that an angle formed by the second guide slope 65b and the width direction is a second inclination angle ⁇ 2, the inclination angles ⁇ 2 of the second guide slopes 65b on both sides in the width direction are the same angle.
  • the protrusion portion 65 is provided at a predetermined position in the flowing direction and the width direction. Specifically, the protrusion portion 65 is disposed at a distance L1, which is equal to or greater than the thickness of the fin part 62, from the end portion of the plate joint part 61 in the flowing direction. In addition, the protrusion portion 65 is disposed at a distance L2, which is equal to or greater than the thickness of the fin part 62, from the fin part 62 in the width direction.
  • some of the fluid circulating in the inner fins 12 in the flowing direction climbs over the step 25 to reach the protrusion portion 65, and flows along the first guide slope 65a.
  • the fluid flowing along the first guide slope 65a of the protrusion portion 65 and the fluid flowing along the plate joint part 61 where the protrusion portion 65 is not provided have different flow velocities. Therefore, a pressure gradient is generated between the fluids, and the pressure gradient generates a cross-sectional secondary flow of which the cross section is a plane perpendicular to the flowing direction. Since the flow velocity of the fluid increases on the inner side of the plate joint part 21 due to the cross-sectional secondary flow, the formation of the thermal boundary layer occurring on the inner side of the plate joint part 21 is inhibited.
  • the protrusion portion 65 has a rectangular shape that is long in the flowing direction, in plan view, but may be disposed as indicated by the dotted line in Fig. 8 . That is, the protrusion portion 65 may have a rectangular shape that is long in a direction oblique to the flowing direction, in plan view. Specifically, assuming that an angle formed by the length direction of the protrusion portion 65 and the flowing direction is an inclination angle ⁇ 3, the inclination angle ⁇ 3 is in a range of 0 degrees to 45 degrees.
  • Fig. 9 is a perspective view illustrating an offset fin of a heat exchanger according to the third embodiment.
  • Fig. 10 is a plan view of the offset fin.
  • Fig. 11 is a sectional view of the offset fin.
  • Fig. 12 is an explanatory diagram regarding a flow of the fluid.
  • a plurality of offset fins 71 in the inner fins 12 are different from the offset fins 15 and 51 of the first and second embodiments.
  • the plurality of offset fins 71 are obtained by replacing the inhibiting part 63 of the second embodiment with an inhibiting part 83. Therefore, the inhibiting part 83 of the offset fin 71 will be explained, and the other parts, that is, a plate joint part 81 and a fin part 82 of the offset fin 71, are the same as the plate joint part 61 and the fin part 62 of the second embodiment. Therefore, the description will be omitted.
  • the inhibiting part 83 is provided on the plate joint part 81. Similar to the first embodiment, the inhibiting part 83 is a part that inhibits the formation of the thermal boundary layer that occurs in the fluid circulating along the inside of the plate joint part 81. Specifically, the inhibiting part 83 is a hole 85 recessed from the plate joint part 81 toward the plate 10. In a case where the plate joint parts 81 are continuous in the offset fins 71 adjacent to each other in the flowing direction, the hole 85 is provided on the plate joint part 81 on the downstream side in the flowing direction. The hole 85 is a through-hole formed through the plate joint part 81. Note that, in the third embodiment, the hole 85 is a through-hole, but may be a hole with a bottom. At least one or more holes 85 are provided in the inner fins 12 in the flowing direction and the width direction.
  • the hole 85 is formed in a rectangular shape in plan view seen from the height direction perpendicular to the flowing direction and to the width direction. Note that, in the third embodiment, the hole 85 has a rectangular shape in plan view, but is not particularly limited to this shape. In plan view, the hole 85 may have a polygonal shape, or may have an annular shape such as a circle or an ellipse. In plan view, the longest length L5 of the hole 85 is equal to or greater than twice the thickness of the fin part 82 and equal to or less than eight times the thickness of the fin part 82.
  • the hole 85 is provided at a predetermined position in the flowing direction and the width direction. Specifically, the hole 85 is disposed at a distance L3, which is equal to or greater than the thickness of the fin part 82, from the end portion of the plate joint part 81 in the flowing direction. In addition, the hole 85 is disposed at a distance L4, which is equal to or greater than the thickness of the fin part 82, from the fin part 82 in the width direction.
  • the plate joint part 81 has a downstream-side slope 81a formed at the end portion on the downstream side in the flowing direction.
  • the downstream-side slope 81a is formed at a part on the downstream side of the plate joint part 81 where no other plate joint part 81 is adjacent thereto on the downstream side in the flowing direction, that is, at a part where a step 88 is formed (refer to the related art of Fig. 12 ) .
  • an angle formed by the downstream-side slope 81a and the flowing direction is a downstream-side inclination angle ⁇ 4
  • the downstream-side inclination angle ⁇ 4 is in a range of 7 degrees to 45 degrees.
  • some of the fluid circulating in the inner fins 12 in the flowing direction climbs over the downstream-side slope 81a to reach the hole 85.
  • the fluid flowing along the plate joint part 81 is separated at the hole 85, thereby initializing the formation of the thermal boundary layer occurring on the inner side of the plate joint part 81.
  • heat exchangers 1, 50, and 70 described in the embodiments described above can be understood as follows, for example.
  • a heat exchanger 1 includes a pair of plates 10 that face each other; and an inner fin 12 which is provided between the pair of plates 10 and in which a fluid circulates, in which the inner fin 12 has a plurality of offset fins 15 which are arranged side by side in a flowing direction of the fluid and are provided such that positions thereof are mutually offset in a width direction perpendicular to the flowing direction, and the offset fin 15 includes a plate joint part 21 which is joined to the plate 10 and has a step 25 formed in the flowing direction, a fin part 22 which is provided along an opposing direction of the pair of plates 10 and is connected to the plate joint part 21, and a reception slope 38 which is provided to the plate joint part 21, obliquely to the flowing direction, and which receives the fluid from the step 25.
  • the reception slope 38 can give the swirling flow R2 to the fluid. Therefore, since the flow velocity increases on the inner side of the plate joint part 21 due to the swirling flow R2, the formation of the thermal boundary layer occurring on the inner side of the plate joint part 21 can be appropriately inhibited. Therefore, since a decrease in heat transfer performance via the plate 10 can be suppressed by reducing the thickness of the thermal boundary layer, a decrease in heat exchange performance of the heat exchanger 1 can be suppressed.
  • the offset fin 15 has a wavy shape in which a part on an upstream side in the flowing direction is set as a top portion 15a, a part on a downstream side in the flowing direction is set as a valley portion 15b, and the top portion 15a and the valley portion 15b are alternately provided along the width direction, and the one of the offset fins 15 adjacent to each other in the flowing direction and the other of the offset fins 15 adjacent to each other in the flowing direction are arranged line-symmetrically with the width direction as an axis of symmetry, and are arranged such that positions thereof are mutually offset in the width direction.
  • the offset fins 15 can be arranged line-symmetrically and offset, only one type of offset fins 15 can be used for the inner fins 12, and the manufacturing cost can be reduced.
  • the offset fins 15 arranged in four rows in the flowing direction are set as one set, the offset fin 15 in a first row and the offset fin 15 in a third row are at the same position in the width direction, the offset fin 15 in a second row is offset to one side in the width direction with respect to the offset fins 15 in the first and third rows, and the offset fin 15 in a fourth row is offset to the other side in the width direction with respect to the offset fins 15 in the first and third rows.
  • the offset fins 15 can be appropriately arranged to inhibit the formation of the thermal boundary layer.
  • the inner fins 12 can be easily configured.
  • a heat exchanger 50 includes a pair of plates 10 that face each other; and an inner fin 12 which is provided between the pair of plates 10 and in which a fluid circulates, in which the inner fin 12 has a plurality of offset fins 51 which are arranged side by side in a flowing direction of the fluid and are provided such that positions thereof are mutually offset in a width direction perpendicular to the flowing direction, and the offset fin 51 includes a plate joint part 61 which is joined to the plate 10, a fin part 62 which is provided along an opposing direction of the pair of plates 10 and is connected to the plate joint part 61, and a protrusion portion 65 which is provided on the plate joint part 61 and protrudes inward from the plate joint part 61.
  • the protrusion portion 65 can give a cross-sectional secondary flow to the fluid. Therefore, since the flow velocity increases on the inner side of the plate joint part 21 due to the cross-sectional secondary flow, the formation of the thermal boundary layer occurring on the inner side of the plate joint part 21 can be appropriately inhibited. Therefore, since a decrease in heat transfer performance via the plate 10 can be suppressed by reducing the thickness of the thermal boundary layer, a decrease in heat exchange performance of the heat exchanger 50 can be suppressed.
  • the protrusion portion 65 is provided on the plate joint part 61 on the upstream side in the flowing direction.
  • the protrusion portion 65 can give a cross-sectional secondary flow to the upstream side in the flowing direction, it is possible to appropriately inhibit the formation of the thermal boundary layer on the downstream side.
  • the protrusion portion 65 has at least one guide slope 65a or 65b among a guide slope 65a that slopes from the upstream side toward the downstream side in the flowing direction, and a guide slope 65b that slopes from one side toward the other side in the width direction.
  • the protrusion portion 65 has an elongated shape in a direction oblique to the flowing direction.
  • the protrusion portion 65 is disposed at a distance L1, which is equal to or greater than a thickness of the fin part 62, from an end portion of the plate joint part 61 in the flowing direction, and the protrusion portion 65 is disposed at a distance L2, which is equal to or greater than the thickness of the fin part 62, from the fin part 62 in the width direction.
  • the protrusion portion 65 can be arranged in an appropriate manner to give a cross-sectional secondary flow to the fluid.
  • a heat exchanger 70 includes a pair of plates 10 that face each other; and an inner fin 12 which is provided between the pair of plates 10 and in which a fluid circulates, in which the inner fin 12 has a plurality of offset fins 71 which are arranged side by side in a flowing direction of the fluid and are provided such that positions thereof are mutually offset in a width direction perpendicular to the flowing direction, and the offset fin 71 includes a plate joint part 81 which is joined to the plate 10, a fin part 82 which is provided along an opposing direction of the pair of plates 10 and is connected to the plate joint part 81, and a hole 85 that is provided to the plate joint part 81 and is recessed from the plate joint part 81 toward the plate 10.
  • the hole 85 can separate the flow of the fluid. Therefore, since the formation of the thermal boundary layer can be initialized by separating the flow of the fluid, the formation of the thermal boundary layer can be appropriately inhibited. Therefore, since a decrease in heat transfer performance via the plate 10 can be suppressed by reducing the thickness of the thermal boundary layer, a decrease in heat exchange performance of the heat exchanger 70 can be suppressed.
  • the hole 85 is provided to the plate joint part 81 on the downstream side in the flowing direction.
  • the formation of the thermal boundary layer can be initialized by the hole 85, on the downstream side where the thermal boundary layer becomes thicker, the formation of the thermal boundary layer on the downstream side can be appropriately inhibited.
  • the hole 85 has a longest length in a plane of the plate 10 of equal to or greater than twice a thickness of the fin part 82 and equal to or less than eight times the thickness of the fin part 82.
  • the size of the hole 85 can be set to an appropriate size that initializes the formation of the thermal boundary layer.
  • the hole 85 is disposed at a distance L3, which is equal to or greater than a thickness of the fin part 82, from an end portion of the plate joint part 81 in the flowing direction, and the hole 85 is disposed at a distance L4, which is equal to or greater than the thickness of the fin part 82, from the fin part 82 in the width direction.
  • the hole 85 can be disposed in an appropriate manner to initialize the formation of the thermal boundary layer.
  • the plate joint part 81 has a downstream-side slope 81a that is formed at an end portion on the downstream side in the flowing direction and slopes toward the plate 10 toward the downstream side in the flowing direction.
  • the fluid flows along the downstream-side slope 81a, and thus, the formation of the separation flow R3 is suppressed. Therefore, since the formation of the separation flow R3 is suppressed, the heat transfer area of the fluid on the downstream side of the plate joint part 81 can be increased, and thus, the heat transfer performance can be improved. In addition, pressure loss can be reduced by suppressing the formation of the separation flow R3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP22864582.6A 2021-08-31 2022-08-30 Wärmetauscher Pending EP4365535A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021141672A JP2023035071A (ja) 2021-08-31 2021-08-31 熱交換器
PCT/JP2022/032653 WO2023033000A1 (ja) 2021-08-31 2022-08-30 熱交換器

Publications (1)

Publication Number Publication Date
EP4365535A1 true EP4365535A1 (de) 2024-05-08

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EP22864582.6A Pending EP4365535A1 (de) 2021-08-31 2022-08-30 Wärmetauscher

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EP (1) EP4365535A1 (de)
JP (1) JP2023035071A (de)
WO (1) WO2023033000A1 (de)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004263881A (ja) * 2003-01-23 2004-09-24 Showa Denko Kk 伝熱フィン、熱交換器、カーエアコン用エバポレータ及びコンデンサ
JP4683111B2 (ja) * 2008-10-17 2011-05-11 株式会社デンソー 排気熱交換装置
JP5609339B2 (ja) 2010-07-09 2014-10-22 株式会社デンソー オイルクーラ
JP2020012589A (ja) * 2018-07-18 2020-01-23 本田技研工業株式会社 熱交換器
JP2021050868A (ja) * 2019-09-25 2021-04-01 株式会社ケーヒン 熱交換器

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WO2023033000A1 (ja) 2023-03-09
JP2023035071A (ja) 2023-03-13

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