WO2018216245A1 - プレート式熱交換器及びヒートポンプ式給湯システム - Google Patents

プレート式熱交換器及びヒートポンプ式給湯システム Download PDF

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Publication number
WO2018216245A1
WO2018216245A1 PCT/JP2017/041468 JP2017041468W WO2018216245A1 WO 2018216245 A1 WO2018216245 A1 WO 2018216245A1 JP 2017041468 W JP2017041468 W JP 2017041468W WO 2018216245 A1 WO2018216245 A1 WO 2018216245A1
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WO
WIPO (PCT)
Prior art keywords
plate
fluid
heat transfer
heat exchanger
transfer plate
Prior art date
Application number
PCT/JP2017/041468
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
佳峰 永島
寿守務 吉村
政博 横井
貴博 堀
匠 白石
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP17910801.4A priority Critical patent/EP3633301A4/en
Priority to JP2019519451A priority patent/JP6735918B2/ja
Priority to US16/614,275 priority patent/US20200072561A1/en
Priority to CN201780090742.XA priority patent/CN110651164B/zh
Publication of WO2018216245A1 publication Critical patent/WO2018216245A1/ja

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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
    • 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
    • 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
    • F28D9/0037—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 conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • 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
    • F28D9/005—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 the plates having openings therein for both heat-exchange media
    • 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
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/0075—Supports for plates or plate assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for conduits

Definitions

  • the present invention relates to a plate type heat exchanger and a heat pump type hot water supply system.
  • Some plate heat exchangers have a structure in which a plurality of heat transfer plates each having a flow path for flowing a fluid are stacked.
  • Patent Document 1 discloses a plate heat exchanger having a configuration in which a plurality of heat transfer plates each having a flow path and a fluid inflow / outflow hole that allows the fluid to flow in / out are communicated with each other. Has been.
  • the flow path is formed in a concave shape having a rectangular shape in plan view.
  • a fluid inflow / outflow hole is adjacent to the recess of the flow path.
  • the inner fin is arrange
  • the fluid outflow / inflow hole is adjacent to the recess of the flow path. For this reason, the fluid tends to flow to a portion of the inner fin adjacent to the fluid inflow / outflow hole. However, it is difficult for the fluid to flow to other portions of the inner fin away from the fluid inflow / outflow holes. As a result, the pressure loss of the fluid is large in the entire inner fin. Thereby, the heat exchange efficiency of a plate type heat exchanger falls.
  • This invention was made in order to solve said subject, and it aims at providing the plate type heat exchanger and heat pump type hot water supply system with high heat exchange efficiency.
  • a plate heat exchanger includes a plate portion in which an outflow / inflow hole for flowing in / out a fluid is formed, and extends to one surface side of the plate portion.
  • a plurality of heat transfer plates each including an outer peripheral wall portion that forms a flow path for allowing a fluid to flow between a plate portion adjacent to one surface side of the plate and an inner fin attached in the flow path.
  • the inner fin is placed on one surface of the plate portion at a position away from the outflow / inflow hole in the flow path, and the entire circumference of the outflow / inflow hole is in contact with the space where the inner fin is not disposed.
  • the inner fin since the inner fin is placed on one surface of the plate portion at a position separated from the outflow / inflow hole in the flow path, the inner fin does not cover the outflow / inflow hole. Further, since the entire circumference of the outflow / inflow hole is in contact with the space where the inner fin is not disposed, a sufficient space for fluid to flow is secured around the outflow / inflow hole. In the present invention, the pressure loss of the fluid is small because the fluid spreads over the entire flow path in the space where the inner fin is not disposed. As a result, the heat exchange efficiency can be increased.
  • FIG. 1 is an exploded perspective view of a plate heat exchanger according to Embodiment 1 of the present invention. Sectional view taken along line II-II shown in FIG. Sectional view taken along line III-III shown in FIG. Sectional view taken along line IV-IV shown in FIG.
  • the front view of the 2nd heat exchanger plate with which the plate type heat exchanger concerning Embodiment 1 of the present invention is provided The enlarged plan view of the edge part of the 1st heat exchanger plate with which the plate type heat exchanger concerning Embodiment 1 of the present invention is provided 8A is a perspective view when viewed from the front, and FIG. 8B is a perspective view when viewed from the back.
  • the enlarged plan view of the edge part of the 2nd heat exchanger plate with which the plate type heat exchanger concerning Embodiment 1 of the present invention is provided In the plate heat exchanger which concerns on Embodiment 1 of this invention, the enlarged plan view which shows the positional relationship of a 1st convex part and a 2nd convex part Sectional drawing of the 1st fluid supply pipe
  • the enlarged plan view of the edge part of the 1st heat exchanger plate with which the plate type heat exchanger concerning Embodiment 2 of the present invention is provided
  • the enlarged plan view of the edge part of the 2nd heat exchanger plate with which the plate type heat exchanger concerning Embodiment 2 of the present invention is provided In the plate type heat exchanger which concerns on Embodiment 2 of this invention, the enlarged plan view which shows the positional relationship of a 1s
  • Sectional drawing which shows the modification of the flange of the 1st tubular wall of the plate type heat exchanger which concerns on Embodiment 1 of this invention, and a 2nd tubular wall Sectional drawing which shows the modification of the 1st fluid supply pipe
  • (F) Perspective view of pin type fin 8A is a rear view when the first convex portion is formed in a circular shape
  • FIG. 8B is a rear view when the first convex portion is formed in a wedge shape
  • the plate-type heat exchanger according to Embodiment 1 exchanges heat between two fluids, and therefore includes a first heat transfer plate in which a flow path for flowing one fluid is formed, and the other fluid.
  • a plate-type heat exchanger in which a second heat transfer plate in which a flow path for flowing is formed is laminated.
  • a space is provided around the fluid inflow / outflow hole formed in the flow path so that the fluid can easily flow through the flow paths of the first heat transfer plate and the second heat transfer plate. Yes.
  • a fluid is flowed to the inner fin provided in the flow path through this space, so that the pressure loss is small.
  • the configuration of the plate heat exchanger will be described with reference to FIGS. In the following description, the two fluids are referred to as a first fluid and a second fluid.
  • FIG. 1 is an exploded perspective view of a plate heat exchanger 1 according to Embodiment 1 of the present invention.
  • 2 is a cross-sectional view taken along the line II-II shown in FIG. 3 is a cross-sectional view taken along line III-III shown in FIG. 4 is a cross-sectional view taken along the line IV-IV shown in FIG. 2 to 4, some of the first heat transfer plate 30 and the second heat transfer plate 40 are omitted from the first heat transfer plate 30 and the second heat transfer plate 40.
  • the plate heat exchanger 1 according to Embodiment 1 includes a first heat transfer plate 30 in which a flow path for flowing the first fluid is formed, the first fluid and the heat.
  • a plurality of second heat transfer plates 40 each having a flow path for flowing a second fluid to be replaced are provided with a laminate 100 in which a plurality of sheets are alternately laminated.
  • the laminated body 100 is sandwiched and reinforced by the first reinforcing plate 10 and the second reinforcing plate 20.
  • the configurations of the plate heat exchanger 1 first, the configurations of the first reinforcing plate 10 and the second reinforcing plate 20 will be described. Next, the configuration of the first heat transfer plate 30 and the second heat transfer plate 40 will be described.
  • the first reinforcing plate 10 is a plate that reinforces the laminated body 100 and is connected to a connecting pipe for supplying and discharging the first fluid and the second fluid that flow through the laminated body 100. As shown in FIG. 1, the first reinforcing plate 10 is formed in a rectangular shape with rounded corners. The first reinforcing plate 10 is arranged parallel to the XZ plane and closest to the + Y side in the plate heat exchanger 1. The first reinforcing plate 10 is provided with a first reinforcing outer peripheral wall portion 11 that surrounds the outer periphery of the first reinforcing plate 10. As shown in FIGS.
  • the first reinforcing outer peripheral wall portion 11 is joined to a second outer peripheral wall portion 41, which will be described later, included in the second heat transfer plate 40 positioned closest to the + Y side in the laminate 100. is doing. Further, the first reinforcing outer peripheral wall portion 11 is formed in a shape that inclines toward the outside of the first reinforcing plate 10 toward the + Y direction from the periphery of the first reinforcing plate 10.
  • a first fluid supply pipe 12 and a second fluid supply pipe 13 for supplying the first fluid and the second fluid to the laminate 100. And are provided.
  • the first fluid supply pipe 12 and the second fluid supply pipe 13 are arranged in the Z direction and extend in the + Y direction.
  • the first fluid supply pipe 12 and the second fluid supply pipe 13 are respectively connected to a connection pipe (not shown) for supplying the first fluid and the second fluid.
  • the first fluid supply pipe 12 and the second fluid supply pipe 13 are supplied with the first fluid and the second fluid, respectively, through these connection pipes.
  • the first fluid flows in the direction indicated by arrow F
  • the second fluid supply pipe 13 the second fluid flows in the direction indicated by arrow S.
  • a first fluid discharge pipe 14 and a second fluid discharge pipe 15 for discharging the first fluid and the second fluid from the laminate 100 are provided at the ⁇ X end of the first reinforcing plate 10. Yes.
  • the first fluid discharge pipe 14 and the second fluid discharge pipe 15 are formed in the same shape as the first fluid supply pipe 12 and the second fluid supply pipe 13 described above.
  • the first fluid discharge pipe 14 and the second fluid discharge pipe 15 are arranged in the Z direction. Each extends in the + Y direction.
  • the first fluid discharge pipe 14 and the second fluid discharge pipe 15 are respectively connected to connection pipes (not shown) for discharging the first fluid and the second fluid. In the first fluid discharge pipe 14 and the second fluid discharge pipe 15, the first fluid and the second fluid are discharged to the connection pipes.
  • the second reinforcing plate 20 is a plate for reinforcing the laminated body 100 that does not include a portion connected to the connection pipe of the first fluid and the second fluid.
  • the second reinforcing plate 20 is formed in a rectangular shape having the same outer shape as the first reinforcing plate 10.
  • the second reinforcing plate 20 is disposed in parallel with the first reinforcing plate 10.
  • the second reinforcing plate 20 is disposed on the most ⁇ Y side in the plate heat exchanger 1, and sandwiches the laminate 100 between the first reinforcing plate 10.
  • the second reinforcing plate 20 Since the second reinforcing plate 20 is joined to the first outer peripheral wall portion 31 of the first heat transfer plate 30 located closest to the ⁇ Y side of the sandwiched laminate 100, the second reinforcing plate 20 surrounds the outer periphery and from the outer periphery to the outer side. A second reinforcing outer peripheral wall portion 21 inclined toward the top is provided. The shape of the second reinforcing outer peripheral wall portion 21 is the same as that of the first reinforcing outer peripheral wall portion 11.
  • FIG. 5 is a front view of the first heat transfer plate 30.
  • FIG. 6 is a cross-sectional view of the first passage holes 33 and 36 and the second passage holes 42 and 45 formed in the first heat transfer plate 30 and the second heat transfer plate 40.
  • FIG. 7 is a front view of the second heat transfer plate 40.
  • the first heat transfer plate 30 is a member for allowing the first fluid to flow in the plate heat exchanger 1. As shown in FIG. 5, the first heat transfer plate 30 includes a plate portion 39 and a first outer peripheral wall portion 31 that surrounds the outer periphery of the plate portion 39.
  • the plate part 39 is formed in a rectangular shape with rounded corners.
  • the shape and size of the plate portion 39 are the same as those of the first reinforcing plate 10 and the second reinforcing plate 20 described above.
  • the first outer peripheral wall portion 31 extends from the outer periphery of the plate portion 39 to the + Y side as shown in FIGS. And the 1st outer peripheral wall part 31 inclines toward the outer side of the plate part 39 as it extends to the + Y side.
  • the + Y end of the first outer peripheral wall portion 31 is in contact with a second outer peripheral wall portion 41 (described later) included in the second heat transfer plate 40 located on the + Y side with respect to the plate portion 39. Thereby, the + Y side of the space formed by the first outer peripheral wall portion 31 surrounding the plate portion 39 is closed.
  • a plurality of such spaces surrounded by the first outer peripheral wall portion 31 are formed.
  • the first fluid is disposed on the + X end side and the ⁇ X end side of the plate portion 39 as shown in FIG.
  • the first fluid inflow / outflow holes 32 and 35 are formed for inflow and outflow.
  • the second heat transfer plate 40 also has a space in which the second outer peripheral wall portion 41 surrounds the plate portion 49.
  • the first passage holes 33 and 36 through which the second fluid flows in and out of the + X end side and the ⁇ X end side of the plate portion 39 are provided. Is formed.
  • the first fluid inflow / outflow holes 32 and 35 are circular holes that penetrate the first heat transfer plate 30 in the Y direction.
  • the first fluid inflow / outflow holes 32 and 35 have the same inner diameter.
  • the first fluid inflow / outflow holes 32 and 35 are formed at positions overlapping the first fluid supply pipe 12 and the first fluid discharge pipe 14 of the first reinforcing plate 10 in the Y direction as shown in FIG. ing.
  • the first passage holes 33 and 36 are circular holes penetrating the first heat transfer plate 30 in the Y direction, and have the same inner diameter as the first fluid inflow / outflow holes 32 and 35.
  • the first passage holes 33 and 36 are arranged on the ⁇ Z side with respect to the first fluid inflow / outflow holes 32 and 35.
  • the 1st passage holes 33 and 36 are formed in the position which overlaps with the 2nd fluid supply pipe 13 and the 2nd fluid discharge pipe 15 of the 1st reinforcement plate 10 seeing in the Y direction, as shown in FIG. .
  • the first passage holes 33 and 36 communicate with a later-described second fluid inflow / outflow hole 46 of the second heat transfer plate 40, so that the first tubular wall is continuous with the inner peripheral wall of the first passage holes 33 and 36.
  • first tubular walls 34 and 37 are provided. As shown in FIG. 6, the first tubular walls 34 and 37 extend in the radial direction from the outer walls of the first tubular walls 34 and 37 to join the plate portion 49 of the second heat transfer plate 40, as shown in FIG. 6.
  • a flange 300 is provided. 1 and 2 to 5 show the first tubular walls 34 and 37 in which the flange 300 is omitted for easy understanding.
  • the second heat transfer plate 40 is a member for flowing the second fluid in the plate heat exchanger 1.
  • the second heat transfer plate 40 includes a plate portion 49 shown in FIG. 7 and a second outer peripheral wall portion 41 that surrounds the outer periphery of the plate portion 49.
  • the plate part 49 is formed in the same shape and size as the plate part 39 of the first heat transfer plate 30.
  • the second outer peripheral wall portion 41 is formed in the same shape and size as the first outer peripheral wall portion 31 of the first heat transfer plate 30.
  • the + Y end of the second outer peripheral wall portion 41 is, as shown in FIGS. 2 to 4, the first reinforcing outer peripheral wall portion 11 or the first reinforcing outer wall portion 11 included in the first reinforcing plate 10 located on the + Y side with respect to the plate portion 49.
  • the heat transfer plate 30 is in contact with the first outer peripheral wall portion 31.
  • the + Y side of the space formed by the second outer peripheral wall portion 41 surrounding the outer periphery of the plate portion 49 is closed by the first reinforcing plate 10 or the first heat transfer plate 30.
  • a plurality of spaces surrounded by such second outer peripheral wall portions 41 are formed.
  • the second fluid In order to circulate the second fluid between the space surrounded by the second outer peripheral wall 41 described above, the second fluid is disposed on the + X end side and the ⁇ X end side of the plate portion 49 as shown in FIG.
  • the second fluid inflow / outflow holes 43 and 46 are formed to allow the inflow and outflow of the fluid.
  • Second passage holes 42 and 45 through which the first fluid flows in and out are formed.
  • the second fluid inflow / outflow holes 43 and 46 are circular holes that penetrate the plate portion 49.
  • the second fluid inflow / outflow holes 43 and 46 have the same inner diameter as the first passage holes 33 and 36.
  • the second fluid inflow / outflow holes 43 and 46 are formed at positions overlapping the second fluid supply pipe 13 and the second fluid discharge pipe 15 of the first reinforcing plate 10 as viewed in the Y direction. Yes.
  • the second fluid inflow / outflow hole 43 when the second fluid is supplied from the second fluid supply pipe 13 into the laminate 100, the second fluid overlaps the first passage hole 33 overlapping in the Y direction view. And smoothly circulates in the Y direction.
  • the second fluid flows in the Y direction, that is, to the second fluid discharge pipe 15 through the first passage hole 36.
  • the second passage holes 42 and 45 are circular holes that penetrate the plate portion 49.
  • the second passage holes 42 and 45 have the same inner diameter as the first fluid inflow / outflow holes 32 and 35.
  • the second passage holes 42 and 45 are formed at positions overlapping the first fluid supply pipe 12 and the first fluid discharge pipe 14 of the first reinforcing plate 10 as viewed in the Y direction.
  • the second passage holes 42 and 45 communicate with the first fluid supply pipe 12, the first fluid discharge pipe 14, or the first fluid inflow / outflow holes 32 and 35, and therefore the inner peripheral walls of the second passage holes 42 and 45.
  • second tubular walls 44 and 47 extending in the + Y direction are provided.
  • the second tubular walls 44 and 47 are provided with flanges 300 having the same shape as the first tubular walls 34 and 37 in order to join with the plate portion 39 of the first heat transfer plate 30. . 1 to 4 and 7, the second tubular walls 44 and 47 in which the flange 300 is omitted are illustrated for easy understanding.
  • FIGS. A first inner fin 38 and a second inner fin 48 are respectively disposed.
  • FIG.5 and FIG.7 in order to prevent the deformation
  • One convex portion 50 and a second convex portion 60 are provided.
  • the 1st inner fin 38, the 2nd inner fin 48, the 1st convex part 50, and the 2nd convex part 60 are demonstrated.
  • FIG. 8 is an enlarged plan view of an end portion of the first heat transfer plate 30.
  • FIG. 9 is a perspective view of the IX region shown in FIG.
  • FIG. 10 is an enlarged plan view of an end portion of the second heat transfer plate 40.
  • FIG. 11 is an enlarged plan view showing the positions of the first convex portion 50 and the second convex portion 60.
  • 9A is a perspective view when the first convex portion 50 is viewed from the front
  • FIG. 9B is a perspective view when the first convex portion 50 is viewed from the back.
  • the first inner fin 38 and the second inner fin 48 have corrugated fin portions that are uneven in the Z direction and extend in the X direction.
  • first inner fin 38 and the second inner fin 48 when the first fluid and the second fluid flow in the X direction, the first fluid and the second fluid flow along the fin portion. Heat of the first fluid and the second fluid is transmitted to the fin portions of the first inner fin 38 and the second inner fin 48, and as a result, the first fluid and the second fluid exchange heat.
  • the wavy fin portions described above are fixed to a substrate portion (not shown) having a rectangular shape in XZ plan view, which each of the first inner fin 38 and the second inner fin 48 has.
  • the length of the substrate portion in the short direction is the first outer peripheral wall portion 31 at the + Z end of the first heat transfer plate 30 and the ⁇ Z end of the first heat transfer plate 30. This is the same as the distance from the first outer peripheral wall portion 31.
  • the length of the substrate portion in the longitudinal direction is smaller than the distance between the first fluid inflow / outflow holes 32 and the first fluid inflow / outflow holes 35 in the X direction.
  • the length of the substrate portion in the short direction is the second outer peripheral wall portion 41 at the + Z end of the second heat transfer plate 40 and the ⁇ Z end of the second heat transfer plate 40. This is the same as the distance from the second outer peripheral wall portion 41.
  • the length of the substrate portion in the longitudinal direction is smaller than the distance between the second fluid inflow / outflow holes 43 and the second fluid inflow / outflow holes 46 in the X direction.
  • substrate part is orient
  • substrate part is orient
  • the first inner fin 38 and the second inner fin 48 are formed as + Y of the first heat transfer plate 30 and the second heat transfer plate 40 as shown in FIGS. 1 to 3, 5, 7, 8, and 10. It is placed on the surface.
  • the + X ends of the first inner fin 38 and the second inner fin 48 are separated from the first fluid inflow / outflow hole 32 and the second fluid inflow / outflow hole 43 in order to facilitate the inflow / outflow of the first fluid and the second fluid. Yes.
  • the first fluid and the second fluid spread in the Z direction when going from the first fluid inflow / outflow hole 32 and the second fluid inflow / outflow hole 43 side to the first inner fin 38 and the second inner fin 48 side.
  • the first fluid and the second fluid tend to flow uniformly over the entire Z direction of the first inner fin 38 and the second inner fin 48. Further, since there is a space in which the first inner fin 38 and the second inner fin 48 are not disposed over the entire circumference of the first fluid inflow / outflow hole 32 and the second fluid outflow / inflow hole 43, the first fluid, The second fluid tends to spread around the first fluid inflow / outflow holes 32 and the second fluid inflow / outflow holes 43.
  • first fluid outflow / inflow hole 35 and the second fluid outflow / inflow hole 46 also have a space in which the first inner fin 38 and the second inner fin 48 are not disposed over the entire circumference.
  • first fluid and the second fluid easily flow from the first inner fin 38 and the second inner fin 48 into the first fluid inflow / outflow hole 35 and the second fluid outflow / inflow hole 46.
  • the diameter of the first fluid inflow / outflow hole 35 and the second fluid outflow / inflow hole 46 is preferably 1/20 to 1/4. These distances are more preferably 1/16 to 1/8 with respect to the diameters of the first fluid inflow / outflow holes 35 and the second fluid inflow / outflow holes 46.
  • these distances may be larger than the pitch in the X direction of the wave of the wavy fin portion of the first inner fin 38 and the second inner fin 48 or the pitch between the fin portion adjacent to the Z direction and the fin portion. Specifically, it is desirable that the pitch is 1.5 to 2.0 times the pitch. The same applies to the distance between the first inner fin 38 and the first fluid inflow / outflow hole 32 and the distance between the second inner fin 48 and the second fluid outflow / inflow hole 43.
  • the first convex portion 50 disposed between the first inner fin 38 and the first fluid outflow / inflow hole 35 has a first convex portion 50 disposed between the first inner fin 38 and the first fluid outflow / inflow hole 32.
  • the same structure as the one convex part 50 is provided.
  • the second convex portion 60 disposed between the second inner fin 48 and the second fluid outflow / inflow hole 46 has a first protrusion disposed between the second inner fin 48 and the second fluid outflow / inflow hole 43.
  • a configuration similar to that of the two convex portions 60 is provided.
  • a plurality of first convex portions 50 are arranged in a region on the first fluid inflow / outflow hole 32 side of the first inner fin 38, that is, in the + X side region on the first heat transfer plate 30. ing.
  • the arrangement of the first protrusions 50 is random because the flow of the first fluid is diffused.
  • Each of the first convex portions 50 protrudes from the + Y surface of the plate portion 39 of the first heat transfer plate 30 to the + Y side.
  • each of the first convex portions 50 is formed in a cylindrical shape whose end, that is, the + Y end is closed.
  • the diameter of the first protrusion 50 is 1/14 to 1/15 of the diameter of the first fluid inflow / outflow hole 32.
  • the diameter of the first convex portion 50 is larger than the distance between the first inner fin 38 and the first fluid outflow / inflow hole 35 and the distance between the second inner fin 48 and the second fluid outflow / inflow hole 46. It is desirable to be small, in particular 2/3 to 1/3 of these distances.
  • the 1st convex part 50 is the state (henceforth the state in which the laminated body 100 was formed) in which the 1st heat-transfer plate 30 and the 2nd heat-transfer plate 40 formed the laminated body 100, and + Y end is 2nd
  • the heat transfer plate 40 is formed at a height that contacts the ⁇ Y surface.
  • the 1st convex part 50 has the shape of the flow path through which a 1st fluid flows as a support
  • the second convex portion 60 includes a plurality of second convex portions 60 in a region on the second fluid inflow / outflow hole 43 side of the second inner fin 48, that is, in the + X side region on the second heat transfer plate 40.
  • the second convex portion 60 is in contact with the ⁇ Y surface of the first heat transfer plate 30 in the state where the first heat transfer plate 30 and the second heat transfer plate 40 form the laminate 100. It is formed at a height.
  • the 2nd convex part 60 has the shape of the flow path through which a 2nd fluid flows as a support
  • connection pipe for supplying the first fluid and the second fluid to be heat exchanged is connected to the plate heat exchanger 1 so that the first fluid and the second fluid are the first fluid supply pipe. 12. It is assumed that the second fluid supply pipe 13 is supplied. Further, the connection pipe for discharging the first fluid and the second fluid is connected to the plate heat exchanger 1, so that the first fluid and the second fluid after the heat exchange are the first fluid discharge pipe 14, It is assumed that the fluid is discharged from the two-fluid discharge pipe 15. In the following description, FIG. 1 is referred to as necessary.
  • FIG. 12 is a cross-sectional view of the first fluid supply pipe 12, the first fluid inflow / outflow hole 32, and the second passage hole 42.
  • the first fluid is supplied to the laminate 100 from the outside via the first fluid supply pipe 12.
  • the supplied first fluid passes through the second passage hole 42 of the second heat transfer plate 40 and the first fluid inflow / outflow hole 32 of the first heat transfer plate 30 in the direction of arrow F, that is, ⁇ Flows in the Y direction.
  • a second tubular wall 44 is formed in the second passage hole 42.
  • the first fluid inflow / outflow hole 32 is not formed with a tubular wall surrounding the outer periphery.
  • the first fluid flows not only in the ⁇ Y direction but also in the direction from the first fluid inflow / outflow hole 32 toward the first inner fin 38 (that is, in the direction of the arrow F1). Thereby, the first fluid flows along the + Y plane of the first heat transfer plate 30.
  • a space where only the first convex portion 50 exists is provided between the first fluid inflow / outflow hole 32 and the first inner fin 38. Therefore, in this space, the first fluid spreads from the first fluid inflow / outflow holes 32 to the entire first heat transfer plate 30 in the Z direction and flows into the first inner fins 38 with a uniform distribution.
  • the first fluid that has flowed into the first inner fin 38 exchanges heat with the first inner fin 38. After heat exchange, the first fluid flows to the first fluid inflow / outflow hole 35 side of the first heat transfer plate 30 (not shown). In the vicinity of the first fluid inflow / outflow hole 35, a space in which only the first convex portion 50 exists is provided between the first inner fin 38. For this reason, the pressure loss of the first fluid is small in this space. As a result, the first fluid flows smoothly toward the first fluid inflow / outflow hole 35 side. On the first fluid inflow / outflow hole 35 side, the ⁇ X end of the first heat transfer plate 30 is closed by the first outer peripheral wall portion 31.
  • the first fluid flows to the first fluid discharge pipe 14 side via the first fluid inflow / outflow hole 35. That is, the first fluid flows to the second passage hole 45 of the second heat transfer plate 40 located on the + Y side. Then, the first fluid flows into the first fluid discharge pipe 14 via the second passage hole 45 and is discharged to the outside.
  • the second fluid is supplied to the stacked body 100 from the outside via the second fluid supply pipe 13 as indicated by an arrow S in FIG.
  • the supplied second fluid flows in the ⁇ Y direction through the second fluid inflow / outflow hole 43 of the second heat transfer plate 40 and the first passage hole 33 of the first heat transfer plate 30.
  • a first tubular wall 34 is formed in the first passage hole 33.
  • the second fluid inflow / outflow hole 43 is not formed with a tubular wall surrounding the outer periphery. Therefore, the second fluid not only flows in the ⁇ Y direction, but also flows from the second fluid inflow / outflow hole 43 to the second inner fin 48 side. Then, the second fluid flows along the + Y plane of the second heat transfer plate 40 and flows into the second inner fin 48.
  • the second fluid that has flowed into the second inner fin 48 exchanges heat with the second inner fin 48. Thereafter, the second fluid flows from the second inner fin 48 to the second fluid inflow / outflow hole 46 side. Since a space where only the second convex portion 60 exists is provided between the second inner fin 48 and the second fluid inflow / outflow hole 46, the second fluid flows in and out of the second fluid with a small pressure loss. It flows to the hole 46 side. On the second fluid inflow / outflow hole 46 side, the + Y end of the second heat transfer plate 40 is closed by the second outer peripheral wall portion 41. On the other hand, a part of the plate surface of the second heat transfer plate 40 is opened by the second fluid inflow / outflow hole 46.
  • the second fluid flows to the second fluid discharge pipe 15 side via the second fluid inflow / outflow hole 46. That is, the second fluid flows to the first passage hole 36 of the first heat transfer plate 30 on the + Y side or the second fluid discharge pipe 15 on the + Y side. Then, the second fluid is discharged to the outside through the second fluid discharge pipe 15.
  • the heat transferred to the first inner fin 38 and the second inner fin 48 is transferred to the first heat transfer plate 30 and the second heat transfer plate 40. Since the first heat transfer plate 30 and the second heat transfer plate 40 are alternately laminated, the heat transferred to the first heat transfer plate 30 and the second heat transfer plate 40 is the first heat transfer plate 30 and the second heat transfer plate 40. Heat exchange is performed between the two heat transfer plates 40. As a result, heat exchange between the first fluid and the second fluid is performed in the plate heat exchanger 1.
  • the first inner fin 38 is separated from the first fluid inflow / outflow holes 32 and 35. Further, the second inner fin 48 is separated from the second fluid inflow / outflow holes 43 and 46.
  • the entire peripheries of the first fluid inflow / outflow holes 32 and 35 and the second fluid outflow / inflow holes 43 and 46 are in contact with a space in which the first inner fin 38 and the second inner fin 48 are not provided. For this reason, in the space between the first inner fin 38 and the first fluid inflow / outflow holes 32, 35, the first fluid spreads over the entire first inner fin 38, and the first fluid passes through the first inner fin 38. It does not flow biased partly.
  • the second fluid spreads over the entire second inner fin 48, and the second fluid passes through the second inner fin 48. It does not flow biased partly. As a result, in the plate heat exchanger 1, the pressure loss between the first fluid and the second fluid is small.
  • a first convex portion 50 is provided between the first inner fin 38 and the first fluid inflow / outflow holes 32 and 35. Further, a second convex portion 60 is provided between the second inner fin 48 and the second fluid inflow / outflow holes 43 and 46 at a position shifted from the first convex portion 50 as viewed in the Y direction. For this reason, in the plate heat exchanger 1, the laminated body 100 is not easily deformed by the pressure of the first fluid and the second fluid. As a result, it can prevent that the laminated body 100 deform
  • the 1st heat transfer plate 30 and the 2nd heat transfer plate 40 are reinforced by the 1st convex part 50 and the 2nd convex part 60 in the part from which a Y direction view differs.
  • the first convex portion 50 and the second convex portion 60 are viewed in the Y direction as compared with the case where the first convex portion 50 and the second convex portion 60 are arranged at the same position or overlapping positions when viewed in the Y direction.
  • the first tubular walls 34 and 37 and the second tubular walls 44 and 47 are provided with flanges 300. For this reason, by joining the flange 300 to the plate surfaces of the first heat transfer plate 30 and the second heat transfer plate 40, the bonding strength between the first tubular walls 34 and 37 and the second heat transfer plate 40, and the first The joint strength between the two tubular walls 44 and 47 and the first heat transfer plate 30 can be increased. As a result, it is possible to prevent the first fluid from leaking from the joint and entering the second flow path, or the second fluid from leaking from the joint and entering the first flow path.
  • the 1st outer peripheral wall part 31 of the 1st heat-transfer plate 30 and the 2nd outer peripheral wall part 41 of the 2nd heat-transfer plate 40 are brazed, and it leaks to the exterior of a 1st fluid and a 2nd fluid. Is prevented. Moreover, the strength of the laminate 100 is increased.
  • the first convex portion 51 is provided in the vicinity of the first fluid inflow / outflow hole 32 and the first passage hole 33.
  • a second convex portion 61 is provided in the vicinity of the second fluid inflow / outflow hole 43 and the second passage hole 42.
  • the first convex portion 51 is provided only in the vicinity of the first fluid inflow / outflow hole 32.
  • the second convex portion 61 is provided only in the vicinity of the second fluid inflow / outflow hole 43.
  • FIG. 13 is an enlarged plan view of an end portion of the first heat transfer plate 30 provided in the plate heat exchanger 2 according to Embodiment 2 of the present invention.
  • FIG. 14 is an enlarged plan view of an end portion of the second heat transfer plate 40 provided in the plate heat exchanger 2 according to Embodiment 2 of the present invention.
  • FIG. 15 is an enlarged plan view showing the positional relationship between the first convex portion 51 and the second convex portion 61 in the plate heat exchanger 2 according to Embodiment 2 of the present invention.
  • the first convex portion 51 is formed only in the + X side and + Z side regions of the first heat transfer plate 30 where the first fluid inflow / outflow holes 32 are formed.
  • a plurality of first convex portions 51 are randomly arranged in the region. The shape and size of each first convex portion 51 are the same as those of the first convex portion 50 of the first embodiment.
  • the second convex portion 61 is formed only in the + X side and ⁇ Z side regions of the second heat transfer plate 40 where the second fluid inflow / outflow holes 43 are formed. .
  • a plurality of second convex portions 61 are also arranged in the region.
  • the shape and size of each of the second convex portions 61 are the same as those of the second convex portion 60 of the first embodiment.
  • the arrangement of the second convex portions 61 is random. However, in the state in which the stacked body 100 is formed, the second convex portion 61 is disposed at a position that does not overlap with the first convex portion 51 as viewed in the Y direction, as shown in FIG.
  • the first convex portions 51 are also randomly arranged in the ⁇ X side and + Z side regions of the first heat transfer plate 30 where the first fluid inflow / outflow holes 35 are formed.
  • the second convex portions 61 are also randomly arranged in the ⁇ X side and ⁇ Z side regions of the second heat transfer plate 40 where the second fluid inflow / outflow holes 46 are formed.
  • the 2nd convex part 61 is arrange
  • FIG. 16 is a conceptual cross-sectional view of the first fluid supply pipe 12 and the second fluid supply pipe 13 of the plate heat exchanger 2 according to Embodiment 2 of the present invention.
  • the first fluid supply pipe 12 and the second fluid supply pipe 13 have connection pipes for supplying the first fluid and the second fluid to be heat exchanged. It is assumed that they are connected.
  • the first convex portion 51 is provided in the vicinity of the first fluid inflow / outflow hole 32, the strength of the pressure resistance of the first flow path is high in the vicinity of the first fluid outflow / inflow hole 32. Hard to do.
  • the first convex portion 51 is not provided in the vicinity of the first passage hole 33 in the first flow path, but in the vicinity of the second fluid inflow / outflow hole 43 in the second flow path adjacent to the first flow path in the Y direction. Is provided with a second convex portion 61. Since it is supported by the second convex portion 61, the vicinity of the first passage hole 33 in the first flow path is also difficult to deform.
  • the first fluid flows smoothly through the first fluid inflow / outflow holes 32 without being hindered by the deformation of the first heat transfer plate 30.
  • the first convex portion 51 is not provided in the vicinity of the first passage hole 33, the first fluid flows from the first fluid inflow / outflow hole 32 to the first passage hole as compared with the case of the first embodiment. It is easier to flow in the vicinity of 33. As a result, the first fluid tends to spread on the ⁇ Z side in the first heat transfer plate 30.
  • the first fluid flows with a more uniform flow rate in the Z direction of the first heat transfer plate 30.
  • the 2nd convex part 61 is provided in the 2nd fluid inflow / outflow hole 43 vicinity, the intensity
  • the 2nd convex part 61 is not provided in the 2nd channel
  • the second fluid smoothly flows through the second fluid inflow / outflow hole 43 without being hindered by the deformation of the second heat transfer plate 40.
  • the second fluid flows from the second fluid inflow / outflow hole 43 to the vicinity of the second passage hole 42 as compared with the first embodiment. It tends to flow more easily in the second heat transfer plate 40 toward the ⁇ Z side.
  • the second fluid flows with a more uniform flow rate in the Z direction of the second heat transfer plate 40.
  • the 1st convex part 51 is provided also in the 1st fluid inflow / outflow hole 35 vicinity of the 1st heat exchanger plate 30 which is not shown in figure.
  • a second convex portion 61 is also provided in the vicinity of the second fluid inflow / outflow hole 46 of the second heat transfer plate 40. For this reason, also in the vicinity of the first fluid inflow / outflow hole 35 and the second fluid inflow / outflow hole 46, the laminated body 100 is hardly deformed, and the first fluid and the second fluid flow smoothly.
  • the first convex portion 51 is not provided in the vicinity of the first passage hole 33.
  • the second convex portions 61 are provided in the vicinity of the adjacent second fluid inflow / outflow holes 43, the deformation of the stacked body 100 can be prevented by a small number of the first convex portions 51.
  • the second convex portion 61 is not provided in the vicinity of the second passage hole 42, but the first convex portion 51 is provided in the vicinity of the adjacent first fluid inflow / outflow hole 32.
  • the convex portion 61 can prevent the laminate 100 from being deformed. As a result, it is possible to prevent the flow of the first fluid and the second fluid from being hindered by the deformation of the stacked body 100.
  • the first convex portion 50 is provided on the first heat transfer plate 30. Further, the second heat transfer plate 40 is provided with a second convex portion 60. On the other hand, in the plate heat exchanger 3 according to the third embodiment, the first convex portion 52 and the second convex portion 62 are provided on the second heat transfer plate 40.
  • the plate heat exchanger 3 according to Embodiment 3 will be described with reference to FIGS. 17 and 18. In the third embodiment, a configuration different from the first and second embodiments will be described.
  • FIG. 17 is an enlarged plan view of an end portion of the second heat transfer plate 40.
  • FIG. 18 is a conceptual cross-sectional view of the first fluid supply pipe 12 and the second fluid supply pipe 13.
  • the dent is hatched.
  • the second heat transfer plate 40 includes a plurality of second protrusions 62 protruding in the + Y direction and a plurality of first protrusions protruding in the ⁇ Y direction as much as the height of the first flow path. 52.
  • each of the 2nd convex part 62 and the 1st convex part 52 is arrange
  • the second convex portion 62 and the first convex portion 52 are disposed in a region on the + X side of the second inner fin 48 in the second heat transfer plate 40. Specifically, the second convex portion 62 and the first convex portion 52 are disposed in the vicinity of the second passage hole 42 and in the vicinity of the second fluid inflow / outflow hole 43.
  • the + Y end of the second convex portion 62 is positioned on the + Y side with respect to the second heat transfer plate 40 having the second convex portion 62 in a state where the laminated body 100 is formed.
  • One reinforcing plate 10 is in contact.
  • the + Y end of the second protrusion 62 is in contact with the first heat transfer plate 30 located on the + Y side with respect to the second heat transfer plate 40 having the second protrusion 62.
  • the 2nd convex part 62 is functioning as a support
  • the ⁇ Y end of the first convex portion 52 is in contact with the first heat transfer plate 30 located on the ⁇ Y side with respect to the second heat transfer plate 40 having the first convex portion 52.
  • the 1st convex part 52 is functioning as a support
  • the second heat transfer plate 40 is also located in a region on the ⁇ X side of the second inner fin 48, that is, the second passage hole 45, the second fluid inflow / outflow of the second heat transfer plate 40. Also in the region on the hole 46 side, the second convex portion 62 and the first convex portion 52 functioning as support columns are provided.
  • the second heat transfer plate 40 has the second protrusion 62 protruding in the + Y direction and the first protrusion protruding in the ⁇ Y direction.
  • a convex portion 52 is provided. Since the 2nd convex part 62 and the 1st convex part 52 function as a support
  • the plate heat exchanger 4 according to the fourth embodiment includes a first protrusion 52 and a second protrusion having the same shape as the second heat transfer plate 40 described in the third embodiment on the first heat transfer plate 30. A portion 62 is provided.
  • the plate heat exchanger 4 according to Embodiment 4 will be described with reference to FIG. In the fourth embodiment, a configuration different from that of the first to third embodiments will be described.
  • FIG. 19 is an enlarged cross-sectional view of the laminate 100.
  • the first heat transfer plate 30 includes a second protrusion 62 protruding in the + Y direction from the plate surface, and a first protrusion 52 protruding in the ⁇ Y direction from the plate surface.
  • the second convex portion 62 and the first convex portion 52 protrude from the plate surface by the same distance.
  • the second heat transfer plate 40 also includes a second convex portion 62 and a first convex portion 52 having the same shape.
  • the 2nd convex part 62 which the 1st heat-transfer plate 30 has, and the 1st convex part 52 which the 2nd heat-transfer plate 40 has are formed in the position which overlaps with a Y direction.
  • the + Y end of the second convex portion 62 included in the first heat transfer plate 30 and the first convex portion 52-Y end included in the second heat transfer plate 40 are in contact with each other and brazed.
  • the 2nd convex part 62 which the 1st heat exchanger plate 30 has, and the 1st convex part 52 which the 2nd heat exchanger plate 40 have are functioning as a support
  • the first convex portion 52 and the second convex portion 62 are on the + X side of the first inner fin 38 of the first heat transfer plate 30. They are arranged in a certain region and a region on the ⁇ X side from the first inner fin 38. Further, the first convex portion 52 and the second convex portion 62 are formed in a region on the + X side of the second heat transfer plate 40 from the second inner fin 48 and a region on the ⁇ X side of the second inner fin 48. Has been placed.
  • the second convex portion 62 included in the first heat transfer plate 30 and the first convex portion 52 included in the second heat transfer plate 40 are provided. It functions as a support for the stacked body 100. For this reason, the 2nd convex part 62 and the 1st convex part 52 can prevent the deformation
  • first convex portion 52 and the second convex portion 62 included in the plate heat exchanger 4 are more convex than the convex portion included in the plate heat exchanger 1-3 according to Embodiment 1-3. Can be halved. For this reason, formation of the 1st convex part 52 and the 2nd convex part 62 is easy, and it is possible to make the board thickness of the 1st heat-transfer plate 30 and the 2nd heat-transfer plate 40 thin.
  • the fifth embodiment is a heat pump hot water supply system 5 in which the plate heat exchanger 1 according to the first embodiment is used. With reference to FIG. 20, heat pump hot water supply system 5 according to Embodiment 5 will be described.
  • FIG. 20 is a block diagram of the heat pump hot water supply system 5. As shown in FIG. 20, the heat pump hot water supply system 5 includes a refrigerant circuit 80 and a water circuit 90 that exchanges heat with the refrigerant circuit 80.
  • the refrigerant circuit 80 includes a compressor 81 that compresses the refrigerant, a plate heat exchanger 1 that exchanges heat between the refrigerant and the water in the water circuit 90, an expansion valve 82, and the refrigerant expanded by the expansion valve 82 from outside air and heat. And a heat exchanger 83 to be exchanged.
  • the compressor 81, the plate heat exchanger 1, the expansion valve 82, and the heat exchanger 83 are connected in this order.
  • the water circuit 90 includes a pump 91 that circulates water and a water supply device 92 for heating and hot water supply.
  • the water circuit 90 is connected to the plate heat exchanger 1.
  • the water circuit 90 includes a heating / hot water supply device 92, a pump 91, and the plate heat exchanger 1.
  • the heating / hot water supply device 92, the pump 91, and the plate heat exchanger 1 are connected in this order to form a closed circuit.
  • the heat pump hot water supply system 5 includes the plate heat exchanger 1. For this reason, the pressure loss of the refrigerant and water is small, and the heat exchange efficiency is high.
  • Embodiment 6 A plate heat exchanger 6 according to Embodiment 6 will be described with reference to FIGS. In the sixth embodiment, a configuration different from that of the first to fifth embodiments will be described.
  • the first fluid is a refrigerant and the second fluid is water.
  • the first fluid flows from the compressor 81 into the inflow hole of the plate heat exchanger 6 in a high-temperature high-pressure gas single-phase state, and the first inner fin 38 (both the fin portions). In a two-phase state in which the gas phase and the liquid phase are mixed.
  • the first fluid flows out from the outflow hole (also referred to as a header portion) of the plate heat exchanger 6 in a high-pressure liquid single-phase state, and returns to the compressor 81 and circulates again.
  • the second fluid is always in a liquid state, absorbs heat from the refrigerant as the first fluid, becomes warm water, is fed into the room, and heats the room.
  • the flow in the refrigerant circuit 80 is reversed by the four-way valve.
  • the first fluid flows from the expansion valve 82 into the outflow hole of the plate heat exchanger 6 in a low-pressure two-phase state, evaporates and absorbs heat at the first inner fin 38, and becomes a two-phase state in which the ratio of the gas phase is increased. .
  • the first fluid is completely gasified and then flows out from the inlet hole of the plate heat exchanger 6 in a gas single phase state.
  • the second fluid is always in a liquid state, and after exchanging heat with the first fluid, water is sent into the room to cool the room.
  • the header part and the fin part are always in the liquid single-phase state, whereas on the first fluid side, the inlet / outlet header part is cooled in the gas and liquid single-phase state when heating is performed.
  • the inlet (outlet in the cooling flow) header portion is in a gas single-phase state, and the outlet (same inlet) header portion is in a two-phase state with a large liquid ratio.
  • FIG. 21 is an enlarged plan view of an end portion of the first heat transfer plate 30 provided in the plate heat exchanger 6 according to Embodiment 6 of the present invention.
  • FIG. 22 is an enlarged plan view of an end portion of the second heat transfer plate 40 provided in the plate heat exchanger 6 according to Embodiment 6 of the present invention.
  • FIG. 23 is an enlarged plan view showing the positional relationship between the first convex portion 53 and the second convex portion 63 in the plate heat exchanger 6 according to Embodiment 6 of the present invention. As shown in FIG.
  • a first convex portion 53 is provided in the vicinity of the first fluid inflow / outflow hole 32 and the first passage hole 33 at the + X end of the first heat transfer plate 30.
  • the same number of first protrusions 53 are also provided in the vicinity of the first fluid inflow / outflow holes 35 and the first passage holes 36 at the ⁇ X end of the first heat transfer plate 30.
  • the number of the second convex portions 63 is smaller than that of the first convex portion 53.
  • the second convex portion 63 is arranged at a position shifted from the first convex portion 53 in the Y direction in a state where the stacked body 100 is formed.
  • the same number of second protrusions 63 are also provided in the vicinity of the second passage hole 45 and the second fluid inflow / outflow hole 46 at the ⁇ X end of the second heat transfer plate 40.
  • the dimples are concentrated on the first fluid side (the dimple generally means a dent, but the dimple shape here is the first (This is the first convex portion 53 formed by denting the -Y surface of the heat transfer plate 30 to the + Y side), so that the performance deterioration of the heat pump hot water supply system 5 as a whole is further reduced. Is possible.
  • the first fluid flows in the gas-liquid two-phase state into the outflow hole on the first fluid side (corresponding to the inflow hole at the time of cooling operation).
  • the first fluid can be brought closer to the single-layer state from the two-phase state.
  • the average heat transfer coefficient on the refrigerant side can be further improved as compared with the first embodiment.
  • the tip of the flange 300 extends in the radial direction from the first tubular walls 34 and 37.
  • the shape of the flange 300 is arbitrary as long as it can be joined to the first heat transfer plate 30 and the second heat transfer plate 40.
  • FIG. 24 is a cross-sectional view showing a modified example of the flanges of the first tubular walls 34 and 37.
  • FIG. 25 is a cross-sectional view showing a modification of the first fluid supply pipe 12, the first fluid inflow / outflow hole 32, and the second passage hole 42.
  • the flange 301 may extend from the + Y end of the first tubular walls 34 and 37 to the inside of the first passage holes 33 and 36.
  • the flange 301 may also be provided on the second tubular walls 44 and 47.
  • the flange 301 provided in the second tubular walls 44 and 47 may extend from the + Y end of the second tubular walls 44 and 47 to the inside of the second passage holes 42 and 45.
  • the flanges 300 and 301 may be referred to as a first flange
  • a flange provided on the second heat transfer plate 40 may be referred to as a second flange.
  • the first inner fin 38 and the second inner fin 48 are formed in a shape having corrugated fin portions that are uneven in the Z direction and extend in the X direction.
  • the first inner fin 38 and the second inner fin 48 are not limited to this.
  • the shape of the fin portion is arbitrary.
  • FIG. 26 shows the first inner fins 38 arranged on the first heat transfer plate 30 provided in the plate heat exchanger 1 according to the first embodiment of the present invention, and the second arranged on the second heat transfer plate 40.
  • 4 is a perspective view of an inner fin 48.
  • FIG. FIGS. 26A to 26F show offset fins, flat plate fins, wave fins, louver fins, corrugated fins, and pin fins, respectively.
  • the fin portions of the first inner fin 38 and the second inner fin 48 may be offset fins in which the inner walls of the grooves shown in FIG.
  • the fin portion may be a flat plate-type fin in which a plurality of flat plates illustrated in FIG.
  • the fin portion may be a corrugated fin having a corrugated fin having a corrugated shape in a plan view as shown in FIGS. 26 (C) to (E).
  • a so-called pin-shaped fin in which pins shown in FIG. 26F are arranged in a lattice pattern may be used.
  • the first convex portion 50-53 and the second convex portion 60-63 are cylindrical. However, in the present invention, the first convex portions 50-53 and the second convex portions 60-63 are formed so as to protrude from the plate surfaces of the first heat transfer plate 30 and the second heat transfer plate 40.
  • the shapes of the first protrusions 50-53 and the second protrusions 60-63 are arbitrary.
  • FIG. 27 is a rear view of the X region shown in FIG.
  • FIG. 27A shows a perspective view when the first convex portion 50 described in the first embodiment is viewed from the back side.
  • FIGS. 27B to 27F respectively show the first convex portion 50 having a wedge shape, an elliptical shape, a triangular shape, a quadrangular shape, and an arc shape as viewed in the Y direction.
  • the first convex portion 50 may be formed in a wedge shape, an elliptical shape, a triangular shape, a quadrangular shape, or an arc shape as viewed in the Y direction as shown in FIGS.
  • the first convex portions 51-53 and the second convex portions 60-63 may also be formed in a wedge shape, an elliptical shape, a triangular shape, a quadrangular shape, and an arc shape as viewed in the Y direction.
  • the front ends of the wedges may be oriented in the direction in which the first fluid and the second fluid flow. In this case, the pressure loss of the first fluid and the second fluid can be further reduced.
  • the diameters of the first convex portion 50 and the second convex portion 60 are 1/14 to 1/15 of the diameter of the first fluid inflow / outflow hole 32.
  • this invention is not limited to this,
  • size of the 1st convex part 50 and the 2nd convex part 60 is arbitrary.
  • the sizes of the first convex portions 51-53 and the second convex portions 61-63 are also arbitrary.
  • FIG. 28 is a plan view showing a modification of the first convex portion 50 of the plate heat exchanger 1 according to Embodiment 1 of the present invention.
  • FIG. 29 is an enlarged plan view showing another modified example of the first convex portion 50 included in the plate heat exchanger 1 according to Embodiment 1 of the present invention.
  • the diameter of the first convex portion 50 may be larger than that in the first embodiment. In this case, the number of first convex portions 50 may be smaller than in the case of the first embodiment.
  • the diameter of the first convex portion 50 may be smaller than that in the first embodiment. In this case, the number of the first convex portions 50 may be larger than that in the first embodiment.
  • the first protrusions 50 may change the size in the Y-direction view, that is, the area in the Y-direction view, depending on the number of the first protrusions 50.
  • the number and area of the first protrusions 50 may be determined according to the required pressure resistance of the stacked body 100. The same applies to the first convex portion 51-53 and the second convex portion 60-63.
  • the plate heat exchanger 1 is used in the heat pump hot water supply system 5.
  • the present invention is not limited to this.
  • the plate heat exchanger 1-4 can also be applied to a cooling chiller. Further, the plate heat exchanger 1-4 can be used for industrial and household equipment such as a power generation device and a food heat sterilization treatment equipment. By using the plate heat exchanger 1-4 for such a device, the heat exchange efficiency can be increased.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2017/041468 2017-05-23 2017-11-17 プレート式熱交換器及びヒートポンプ式給湯システム WO2018216245A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP17910801.4A EP3633301A4 (en) 2017-05-23 2017-11-17 PLATE HEAT EXCHANGER AND HEAT PUMP HOT WATER SUPPLY SYSTEM
JP2019519451A JP6735918B2 (ja) 2017-05-23 2017-11-17 プレート式熱交換器及びヒートポンプ式給湯システム
US16/614,275 US20200072561A1 (en) 2017-05-23 2017-11-17 Plate heat exchanger and heat pump hot water supply system
CN201780090742.XA CN110651164B (zh) 2017-05-23 2017-11-17 板式热交换器及热泵式供热水系统

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JP2017101390 2017-05-23
JP2017-101390 2017-05-23

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US (1) US20200072561A1 (zh)
EP (1) EP3633301A4 (zh)
JP (1) JP6735918B2 (zh)
CN (1) CN110651164B (zh)
WO (1) WO2018216245A1 (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020161727A1 (en) * 2019-02-05 2020-08-13 Pranav Vikas India Pvt Limited Universal heat exchanger
CN113196002A (zh) * 2018-12-27 2021-07-30 翰昂汽车零部件有限公司 换热器
JP7416854B2 (ja) 2021-05-06 2024-01-17 コミッサリア ア レネルジー アトミーク エ オ ゼネルジ ザルタナテイヴ スタッドにより形成された少なくとも１つの流体供給分配ゾーンを組み込んだチャネルを備えるプレートを有するタイプの熱交換器モジュール

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WO2020161727A1 (en) * 2019-02-05 2020-08-13 Pranav Vikas India Pvt Limited Universal heat exchanger
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